DE102014218610A1 - Power-shiftable multi-speed transmission in planetary design - Google Patents

Abstract

The transmission comprises three planetary gear sets (RS1, RS2, RS3) and six rotatable shafts (1, 2, 3, 4, 5, 6), wherein the sun gear of a first planetary gear set (RS1) is connected to a fourth shaft (4) can be coupled to a housing (G) via a brake (04) and can be connected via a fourth clutch (46) to a sixth shaft (6) which is connected to the ring gear of a second planetary gear set (RS2) and via a second clutch (26). with the output shaft (2) is releasably connectable, which is connected to the web of a third planetary gear set (RS3) and the ring gear of the first planetary gear set (RS1), wherein a sixth shaft (6) connected to the rotor of an electric machine (EM) or operatively connected and a third shaft (3) is connected to the web of the second planetary gear set (RS2) and the ring gear of the third planetary gear set (RS3), wherein the drive shaft (1) connected to the web of the first planetary gear set (RS1) and via a first clutch (15) with it is releasably connectable to the ring gear of the second planetary gear set (RS2) connected fifth shaft (5), wherein the sun gear of the third planetary gear set (RS3) is coupled to the housing (G) and wherein a third clutch (36, 35, 56) is provided is, by closing the second planetary gear set (RS2) is blockable.

Description

The present invention relates to a powershiftable multi-speed transmission in planetary design with integrated electric machine for a hybrid drive of a motor vehicle according to the preamble of patent claim 1.

Automatic transmissions, particularly for motor vehicles, include, in the prior art, planetary gear sets that are switched by means of friction elements, such as clutches and brakes, and usually with a slip element and optionally a lockup clutch, such as a hydrodynamic torque converter or a fluid coupling connected.

Automatically switchable vehicle transmissions in planetary construction in general are already widely described in the prior art and are subject to permanent development and improvement. Thus, these transmissions require a low construction cost, in particular a small number of switching elements, and in the case of sequential switching, double circuits, i. avoid switching on or off of two switching elements, so that in circuits in defined gear groups only one switching element is changed. Furthermore, to be reduced by means of such transmission of fuel consumption, which can be done on the one hand by reducing the internal transmission losses and on the other hand by operating the engine at the ideal operating point. In order to operate the internal combustion engine at its ideal operating point, it is particularly important to realize small gear jumps with a large gear spread, which results in the increase of the number of gears.

From the DE 10 2012 212 257 A1 the assignee is a powershiftable planetary gearbox for a hybrid drive of a motor vehicle, with three coupled simple minus planetary gear sets, multiple switching elements and at least one electric machine, which is associated with a shaft within the transmission, wherein in a first planetary gear, the ring gear with a housing Component connectable and the planet carrier is drivingly connected to the ring gear of a second planetary gear, wherein in the second planetary gear set of the planet carrier connected to the ring gear of a third planetary gear and the sun gear is driven by a transmission input shaft and wherein in the third planetary gear set of the planet carrier is connected to a transmission output shaft. A simple minus planetary gear known to include a sun gear, a ring gear and a ridge on which planet gears are rotatably mounted, each meshing with the sun gear and ring gear. In this way, the ring gear at a fixed web on a sun gear opposite direction of rotation. In contrast, a simple plus planetary gear includes a sun gear, a ring gear and a web on which inner and outer planetary gears are rotatably mounted, wherein all inner planetary gears mesh with the sun gear and all outer planetary gears with the ring gear, each inner planetary gear each having an outer Planet wheel meshes. As a result, the ring gear has the same direction of rotation when the web is held on as the sun gear and there is a positive stationary gear ratio.

In the known transmission it is provided that the switching elements can be designed as claw switching elements that the sun gear of the first planetary gear set is connected to the housing-fixed component and that the sun gear of the third planetary gear set with the housing-fixed component and with the ring gear of the first planetary gear set is connectable.

With the help of the electric machine is a traction power in circuits in hybrid operation, with an electro-dynamic starting (EDA operation) is possible. In this case, over one or more planetary gear sets of the transmission, a speed superposition of the rotational speed of the engine, the speed of the electric machine and the transmission output shaft speed is achieved, so that starting from standstill while the internal combustion engine is possible, the electric machine with a suitable for the starting counter torque a torque of Internal combustion engine supported.

Further, in the known transmission, the circuits 2-3 and 3-4 are carried out such that the electric machine is connected to the output with a fixed ratio and the traction is supported only by electric motor, while in the background by the internal combustion engine, a load-free circuit as in an automated Manual transmission is executed. Such, so-called output-driven circuits can lead to a reduction in driving performance during the circuit when the internal combustion engine is designed to be more powerful in relation to the electric machine.

In addition, the circuits 1-2 and 4-5 are performed such that in the context of an electrodynamic circuit (EDS), also called EDA circuit, analogous to the electrodynamic approach via one or more planetary gear sets a speed superposition of the speed of the engine, the speed of the electric machine and the transmission output shaft speed is achieved, wherein at the start of the circuit, the torques of the electric machine and the Internal combustion engine can be adjusted so that the switching element to be interpreted is free of load. After opening the switching element to be interpreted, a rotational speed adjustment takes place while maintaining the tensile force, such that the switching element to be engaged is synchronized, whereby after closing the switching element to be engaged, the load distribution between the internal combustion engine and the electric machine takes place depending on the hybrid operating strategy. In such circuits, since the driving performance is applied by the engine and the electric machine, there is no reduction in running performance during the shift.

In the from the DE 10 2012 212 257 A1 known transmission can be realized with two translations ie two electric motor driven gears, in purely electric driving advantageously the transmission input shaft does not rotate, thereby eliminating the need for an additional clutch for separating the engine from the drive train. The gears of purely electric driving are needed to realize a reverse gear, since the transmission has no mechanical reverse gear. Here, in one of the two possible gears of the purely electric driving the engine in the gears 2, 3 or 4 can be connected by closing each another switching element without interruption of traction, wherein the starting of the internal combustion engine can be done for example by means of a separate starter. Disadvantageously, however, the internal combustion engine in the other gear of the purely electric driving operation can only be connected with traction interruption, since the transmission input shaft is braked in this gear.

The present invention has for its object, starting from the cited prior art to specify a power shift planetary gear with integrated electric machine for a hybrid drive of a motor vehicle, which has at least five mechanical forward gears and two forward gears in purely electric driving, in all available gears in purely electric driving the internal combustion engine in the most appropriate aisles can be added while maintaining the traction. Furthermore, the construction cost, the component load and the size to be optimized and also the efficiency in terms of drag and gearing losses can be improved.

This object is achieved by the features of claim 1. Further advantages and advantageous embodiments will become apparent from the dependent claims.

Accordingly, an inventive powershiftable multi-speed transmission in planetary design with integrated electric machine for a hybrid drive of a motor vehicle is proposed, which has a drive and an output, which are arranged in a housing. Furthermore, three planetary gear sets, hereinafter referred to as the first, second and third planetary gear set, six rotatable shafts - hereinafter referred to as drive shaft, output shaft, third, fourth, fifth and sixth shaft - and at least five preferably designed as a form-locking switching elements switching elements, comprising a Brake and four clutches, provided, the selective intervention causes different ratios between the drive and the output.

The planetary gear sets of the transmission are preferably designed as negative planetary gear sets.

According to the invention, the sun gear of the first planetary gear is rotatably connected to the fourth shaft, which is releasably connectable via the brake of the transmission to a housing of the transmission and via a fourth clutch with the sixth shaft, which rotatably connected to the ring gear of the second planetary gear set and the rotor of the electric machine rotatably connected or via a component for generating a constant pretranslation, such as another planetary gear, a spur gear or a chain or belt drive is operatively connected and releasably connectable via a second clutch to the output shaft of the transmission.

The third shaft is rotatably connected to the web of the second planetary gear set and the ring gear of the third planetary gear set, wherein the output shaft is rotatably connected to the web of the third planetary gear set and the ring gear of the first planetary gear set. Furthermore, the drive shaft of the transmission with the web of the first planetary gearset is rotatably connected and releasably connectable via a first clutch with the non-rotatably connected to the ring gear of the second planetary gear fifth shaft, wherein the sun gear of the third planetary gear set is coupled to the housing. According to the invention, a third clutch is provided by the closing of the second planetary gear set is blockable.

The third clutch can be designed according to a first embodiment of the invention as a coupling which connects the sixth shaft with the third shaft and thus the ring gear with the web of the second planetary gear set releasably. In the context of a further embodiment, the third clutch can be designed as a coupling which the sixth shaft with the fifth shaft and thus the ring gear with the sun gear of the second The planetary gear set detachably connects. Alternatively, the third clutch may be embodied as a clutch which releasably connects the third shaft with the fifth shaft and thus the web with the sun gear of the second planetary gear set.

In order to enable a coaxial arrangement of the drive and output shafts, the planetary gear sets are considered axially on the drive side in the direction of force flow in the train operation of the internal combustion engine, which is connectable to the transmission, arranged in the order of first planetary gear set, second planetary gear set, third planetary gear set, for the purpose of a front -Quer- or rear-transverse arrangement, the order considered axially on the drive side in the direction of power flow in the train operation of the internal combustion engine, which is connectable to the transmission, third planetary, first planetary, second planetary gear is.

In this embodiment, five forward mechanical speeds, i. internal combustion engine gears and two forward gears in purely electric driving feasible, the first forward gear can be switched by closing the first clutch via an EDA circuit, which is approached electrodynamically. In this case, a rotational speed superposition of the rotational speed of the internal combustion engine, the rotational speed of the electric machine and the transmission output shaft speed is achieved, so that starting from standstill is possible with the internal combustion engine running, wherein the electric machine with a suitable for the starting process counter torque torque of the engine is supported. The five achievable mechanical forward gears then correspond to the forward gears 2-6 of the transmission.

According to one embodiment of the invention, a further brake can be provided by the closing of the sixth shaft of the transmission can be coupled to a housing of the transmission. In this variant, six forward mechanical gears, i. Internal combustion engine gears and two forward gears can be realized with purely electric driving.

According to the invention, in the context of functionally identical variants, at least one of the planetary gear sets of the transmission embodied as minus planetary gear sets can be designed as a positive planetary gear set, if the web and ring gear connection are exchanged at the same time and the amount of the stationary gear ratio compared to the embodiment as a minus planetary gearset increased by 1.

In the context of further embodiments of the transmission according to the invention two switching elements can each be combined in a double switching element, if these switching elements have a common shaft and do not have to be switched simultaneously in one of the gears.

The inventive design of the multi-speed transmission results in particular for passenger cars suitable translations and increased overall spread, causing an improvement in ride comfort and a significant consumption reduction can be effected.

In addition, the construction cost is significantly reduced with the multi-stage transmission according to the invention by a small number of switching elements and planetary gear sets. Furthermore, in the multistage transmission according to the invention, a good efficiency in the main drives with respect to the drag and gear losses.

In addition, the transmission according to the invention is designed such that an adaptability to different drive train configurations is made possible both in the power flow direction as well as in space. The transmission can be installed, for example, in front-transverse design or as part of a standard drive.

The invention will be explained in more detail below by way of example with reference to the attached figures. These are:

1 a schematic view of a preferred embodiment of a multi-speed transmission according to the invention;

2 : an exemplary circuit diagram for a multi-step transmission according to 1 ;

3 a schematic view of a second preferred embodiment of a multi-speed transmission according to the invention;

4 a schematic view of a third preferred embodiment of a multi-speed transmission according to the invention;

5 a schematic view of a further preferred embodiment of a multi-speed transmission according to the invention;

6 a schematic view of a further preferred embodiment of a multi-speed transmission according to the invention;

7 a schematic view of a further preferred embodiment of a multi-speed transmission according to the invention;

8th a schematic view of a further preferred embodiment of a multi-speed transmission according to the invention;

9 : an exemplary circuit diagram for a multi-step transmission according to 8th ;

10 a schematic view of a further preferred embodiment of a multi-speed transmission according to the invention;

11 a schematic view of a further preferred embodiment of a multi-speed transmission according to the invention;

12 a schematic view of a further preferred embodiment of a multi-speed transmission according to the invention;

13 a schematic view of a further preferred embodiment of a multi-speed transmission according to the invention; and

14 : a schematic view of another preferred embodiment of a multi-speed transmission according to the invention.

In 1 is an inventive multi-stage transmission with a drive shaft 1 , an output shaft 2 and three planetary gear sets RS1, RS2 and RS3, which are arranged in a housing G. At the in 1 As shown, the planetary gear sets are designed as negative planetary gear sets. According to the invention, in the context of functionally equivalent variants, at least one of the according to 1 Planetary gear sets designed as negative planetary gear sets can be designed as a plus planetary gear set, if at the same time the web and ring gear connection are exchanged and the amount of the stationary gear ratio is increased by 1 compared to the design as minus planetary gear set.

In the embodiment shown, the planetary gear sets RS1, RS2, RS3 axially view the drive side in the direction of force flow in the train operation of the internal combustion engine, which is connectable to the transmission arranged in the order of first planetary gear set RS1, second planetary gear set RS2, third planetary gear set RS3, wherein a coaxial arrangement of Drive and output shaft is made possible. According to the invention, the axial order of the individual planetary gear sets and the arrangement of the switching elements are freely selectable, as long as it allows the binding of the elements.

How out 1 can be seen, five switching elements, namely a brake 04 and four clutches 15 . 26 . 36 . 46 intended. The spatial arrangement of the switching elements can be arbitrary and is limited only by the dimensions and the external shape. The clutches and the brake of the transmission are preferably designed as form-locking switching elements, for example as claw switching elements or synchronizers, however, individual or all switching elements can be embodied as friction shifting elements or lamellar switching elements within the scope of further embodiments.

With these switching elements a selective switching of five mechanical, ie internal combustion engine forward gears can be realized. The multi-speed transmission according to the invention has a total of six rotatable shafts, which are referred to below as the drive shaft, output shaft, third, fourth, fifth and sixth shaft, wherein the drive shaft, the first shaft 1 and the output shaft, the second shaft 2 of the transmission.

According to the invention in the multi-stage transmission according to 1 provided that the sun gear of the first planetary gear set RS1 with the fourth wave 4 rotatably connected, which via the brake 04 can be coupled to a housing G of the transmission and a fourth clutch 46 with the sixth wave 6 is releasably connectable, which rotatably connected to the ring gear of the second planetary gear set RS2 and a second clutch 26 with the output shaft 2 the transmission is releasably connectable, which is rotatably connected to the web of the third planetary gearset RS3 and the ring gear of the first planetary gearset RS1.

According to the invention and referring to 1 is the sixth wave 6 rotatably connected to the rotor of an electric machine EM. In the context of further embodiments, the sixth wave 6 be operatively connected to the electric machine EM via a component for generating a constant pretranslation, for example, a further planetary gear, whereby an advantageous design of the electric machine with respect to the speeds and the torque can be achieved. For example, can be increased by the choice of a suitable translation of the component to produce a constant pretranslation, the rotational speeds of the electric motor EM and the torque can be reduced. Furthermore, the sixth wave 6 to be operatively connected to the rotor of the electric machine EM via a spur gear or a chain or belt drive to realize an axially parallel, lateral arrangement of the electric machine EM.

The third wave 3 of the transmission is rotatably connected to the web of the second planetary gearset RS2 and the ring gear of the third planetary gearset RS3. According to the invention, the drive shaft 1 the transmission with the web of the first planetary gear set RS1 rotatably connected and via a first clutch 15 with the fifth shaft rotatably connected to the ring gear of the second planetary gearset RS2 5 releasably connectable, wherein the sun gear of the third planetary gear set RS3 is coupled to the housing G (shaft 0 ). According to the invention, a third clutch is provided by the Close the second planetary gearset RS2 is blockable. In the example shown, the third clutch is a clutch 36 executed, which is the sixth wave 6 with the third wave 3 and thus the ring gear with the web of the second planetary gear set RS2 releasably connects.

In the gear shown, the brake 04 and the fourth clutch 46 and / or the second and third clutches 26 . 36 each combined in a double switching element with a common actuator, since these switching elements have a common shaft and do not have to be switched simultaneously in one of the gears. This results in an advantageous manner in a low construction cost and correspondingly lower costs.

In 2 is an exemplary circuit diagram of a multi-speed transmission according to 1 shown. The multistage transmission has five forward mechanical speeds which, in the example shown, form the forward gears 2-6 of the transmission. For every mechanical forward gear two switching elements are closed. Out 2 It will be seen that in sequential shifting of the mechanical forward gears only one switching element is switched on and one switching element has to be switched off, since two adjacent gear stages share a switching element. Furthermore, the transmission has two electric motor driven forward gears, ie gears in the purely electric driving operation, in 2 are designated E1 and E2.

The first forward gear EDA of the transmission is in the example shown by closing the first clutch 15 switched via an EDA interconnection, which is approached electrodynamically until the second forward gear is engaged. In this case, in the second and third planetary gear set RS2, RS3, a rotational speed superposition of the rotational speed of the internal combustion engine, the rotational speed of the electric machine EM and the transmission output shaft speed is achieved, so that starting from standstill while the engine is running is possible, wherein the electric machine with a suitable for the starting counter torque Torque of the engine is supported. Furthermore, in the EDA mode, it is possible to move to the second, third or fourth forward gear, the EDA mode being terminated by closing the further gear element assigned to the respective gear, and the corresponding forward gear of the transmission being switched. By closing the second, third or fourth clutch 26 . 36 . 46 Thus, the second, third and fourth forward gear is switched.

The second forward speed results from closing the first and second clutches 15 . 26 , the third forward speed by closing the first and third clutch 15 . 36 , the fourth forward gear by closing the first and fourth clutch 15 . 46 , the fifth forward speed by closing the second and fourth clutch 26 . 46 and the sixth forward speed is achieved by closing the brake 04 and the second clutch 26 , To realize at least one reverse gear, the gears of the purely electric driving operation are switched when the direction of rotation of the electric machine EM. According to the invention, even with the same transmission scheme depending on the switching logic different gear jumps, so that an application or vehicle-specific variation is possible.

The first electric motor driven forward gear E1 is obtained by closing the third clutch 36 wherein in this gear, an addition of the internal combustion engine while maintaining the tensile force by closing the first clutch 15 can be carried out; This results in the third forward gear. The second electric motor driven forward gear E2 is obtained by closing the second clutch 26 wherein in this gear, an addition of the internal combustion engine while maintaining the tensile force in the second forward gear by closing the first clutch 15 , in the fifth forward gear by closing the fourth clutch 46 and in the sixth forward by closing the brake 04 can be carried out.

Advantageously, the circuits from the second to the third forward gear, from the third to the fourth forward gear and from the fourth to the fifth forward gear as load circuits, namely as electrodynamic circuits (EDS) are performed, via one or more planetary gear sets of the transmission, a rotational speed superposition of Speed of the internal combustion engine, the speed of the electric machine and the transmission output shaft speed is achieved, at the beginning of the circuit, the torques of the electric machine and the internal combustion engine are adjusted so that the switching element to be interpreted load and after the opening of the switching element auszulegenden a speed adjustment while maintaining the tensile force, so in that the switching element to be engaged is synchronized, whereby after the closing of the switching element to be engaged, the load sharing between the internal combustion engine and the electric machine takes place according to the hybrid operating strategy. When switching from the second to the third forward gear and the third to the fourth forward gear, the first clutch remains 15 closed, wherein in the circuit from the fourth to the fifth forward gear, the fourth clutch 46 remains closed.

The circuit from the fifth to the sixth forward gear is driven by the electric machine EM, wherein the second clutch 26 remains closed. Thus, all circuits except for the circuit from the fifth to the sixth forward gear electrodynamic circuits in which good performance can be achieved even during the circuit. In the circuit from the fifth to the sixth forward gear, the driving performance during the circuit is no longer of particular importance, since the highest gear is usually designed as a smooth gear, which is used only for driving requirements below the maximum mileage.

Due to the design according to the invention, the traction force is maintained in an advantageous manner by means of the electric machine EM of the transmission in all circuits. This results in a reduction in drag losses and the elimination of the need for a starting clutch or a torque converter with lock-up clutch.

This in 3 Example shown differs from the embodiment according to 1 in that the third clutch, by the closing of which the second planetary gear set RS2 is lockable, as a clutch 56 which is the sixth wave 6 with the fifth wave 5 and thus the ring gear with the sun gear of the second planetary gear set RS2 releasably connects. The circuit diagram corresponding to this embodiment corresponds to the circuit diagram according to 2 with the difference that the reference number 36 for the third clutch by the reference numeral 56 is replaced.

Alternatively, the third clutch as a clutch 35 be executed, which is the third wave 3 with the fifth wave 5 and thus releasably connects the web with the sun gear of the second planetary gearset RS2. This embodiment is the subject of 4 , The circuit diagram corresponding to this embodiment corresponds to the circuit diagram according to 2 with the difference that the reference number 36 for the third clutch by the reference numeral 35 is replaced.

In 5 An embodiment of the transmission according to the invention is shown, which differs from the embodiment according to 1 differs in that the planetary gear seen axially on the drive side in the direction of force flow in the train operation of the internal combustion engine, which is connectable to the transmission, in the order third planetary RS3, first planetary RS1, second planetary RS2 are arranged, creating a front-transverse or rear cross Arrangement of the transmission is possible, wherein 6 shows a transmission, which is from the transmission according to 3 by the axial order third planetary gearset RS3, first planetary gearset RS1, second planetary gearset RS2 results. Subject of the 7 is an embodiment of the invention, which differs from the embodiment according to 4 differs in that the planetary gear sets are axially arranged in the order of the third planetary gearset RS3, the first planetary gear set RS1, second planetary gearset RS2 are arranged. Due to the different arrangement of the planetary gear sets, the circuit diagrams remain unchanged.

According to a further embodiment of the invention, the subject of the 8th is, is starting from a transmission according to 1 another brake 06 provided, which is preferably designed as a positive switching element, by closing the sixth wave 6 of the transmission to a housing G of the transmission can be coupled. In this variant, six mechanical forward gears, ie internal combustion engine gears and two forward gears in purely electric driving can be realized, as shown in the corresponding exemplary circuit diagram according to 9 seen.

The circuit diagram differs from the circuit diagram according to 2 in that six mechanical forward gears are possible, which form the forward gears 1-6 of the transmission. The additional mechanical forward gear is obtained by closing the additional brake 06 and the first clutch 15 and forms the first forward gear of the transmission, so that the first forward speed is not achieved by closing the first clutch 15 is switched via an EDA interconnection. The remaining forward gears 2-6 and the electric motor-driven forward gears E1 and E2 correspond to the gears 2-6 and E1 and E2 according to the circuit diagram 2 ,

Advantageously, in addition to the circuits 2-3, 3-4, 4-5, the circuit from the first to the second forward gear as a load circuit, namely as electrodynamic circuit (EDS), are executed, wherein the first clutch 15 remains closed. Furthermore, an EDA startup is possible, for which purpose the first clutch 15 is closed. The EDA operation can be completed by closing the additional brake 06 be terminated by inserting the first forward gear. In addition, in the EDA mode can be driven to the second, third or fourth forward gear, which closes by closing the further, the respective gear associated switching element of the EDA operation and the corresponding forward gear of the transmission is switched. By closing the second, third or fourth clutch 26 . 36 . 46 Thus, the second, third and fourth forward gear is switched.

At the in 8th shown gear can eg the brake 04 and the fourth clutch 46 and / or the second and third clutches 26 . 36 or the brakes 04 . 06 or the second clutch 26 and the further brake 06 or the further brake 06 and the third clutch 36 or the further brake 06 and the fourth clutch 46 each combined in a double switching element with a common actuator, since these switching elements have a common shaft and do not have to be switched simultaneously in one of the gears. This results in an advantageous manner in a low construction cost and correspondingly lower costs.

This in 10 Example shown differs from the embodiment according to 8th with unchanged operation in that the third clutch, by the closing of the second planetary gearset RS2 is blockable, as a clutch 56 which is the sixth wave 6 with the fifth wave 5 and thus the ring gear with the sun gear of the second planetary gear set RS2 releasably connects. The circuit diagram corresponding to this embodiment corresponds to the circuit diagram according to 9 with the difference that the reference number 36 for the third clutch by the reference numeral 56 is replaced.

According to a variant of the invention, the third clutch as a clutch 35 be executed, which is the third wave 3 with the fifth wave 5 and thus releasably connects the web to the sun gear of the second planetary gearset RS2 as described 11 illustrated. The circuit diagram corresponding to this embodiment corresponds to the circuit diagram according to 8th with the difference that the reference number 36 for the third clutch by the reference numeral 35 is replaced.

In 12 An embodiment of the transmission according to the invention is shown, which differs from the embodiment according to 8th is different in that the planetary gear sets axially arranged in the order of the third planetary RS3, first planetary RS1, second planetary RS2 are arranged, whereby a front-transverse or rear-transverse arrangement of the transmission is possible 13 shows a transmission, which is from the transmission according to 10 by the axial order third planetary gearset RS3, first planetary gearset RS1, second planetary gearset RS2 results. In 14 an embodiment of the invention is shown, which differs from the embodiment according to 11 differs in that the planetary gear sets for realizing a front-transverse or rear-transverse arrangement of the transmission axially arranged in the order of the third planetary gearset RS3, first planetary gearset RS1, second planetary gearset RS2 are arranged. Due to the different arrangement of the planetary gear sets, the circuit diagrams remain unchanged.

As already stated, at least one of the planetary gear sets of the transmission designed as minus planetary gear sets in the examples shown can be designed as a plus planetary gear set, if the web and ring gear connection are exchanged at the same time and the amount of the stationary gear ratio compared to the embodiment as a minus planetary gear set 1 is increased. For example, in the embodiment according to 1 the second planetary gear set RS2 be designed as a plus planetary gear set, if otherwise unchanged transmission structure, the sixth wave 6 with the bridge and the third wave 3 are rotatably connected to the ring gear of the second planetary gearset RS2. To the same translations as in the execution according to 1 to achieve otherwise unchanged gear assembly, the amount of stationary gear ratio of the second planetary gear set RS2 is increased by 1 compared to the design as a minus planetary gear set.

According to the invention, it is also optionally possible to provide additional freewheels at any suitable location of the multi-speed transmission, for example between a shaft and the housing or, if necessary, to connect two shafts.

On the drive side or on the output side, an axle differential and / or a distributor differential can be arranged.

The multistage transmission according to the invention also allows the arrangement of a torsional vibration damper between the drive motor and transmission.

In the context of a further, not shown embodiment of the invention can on each shaft, preferably on the drive shaft 1 or the output shaft 2 , a wear-free brake, such as a hydraulic or electric retarder or the like, be arranged, which is particularly important for use in commercial vehicles of particular importance. Furthermore, for driving additional units on each shaft, preferably on the drive shaft 1 or the output shaft 2 be provided a power take-off.

LIST OF REFERENCE NUMBERS

0

wave

1

first shaft, drive shaft

2

second shaft, output shaft

3

third wave

4

fourth wave

5

fifth wave

6

sixth wave

04

brake

06

more brake

15

first clutch

26

second clutch

35

third clutch

36

third clutch

46

fourth clutch

56

third clutch

EM

electric machine

G

casing

RS1

first planetary gear set

RS2

second planetary gear set

RS3

third planetary gear set

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 102012212257 A1 [0004, 0009]

Claims (13)

Powershiftable multi-speed transmission in planetary design with integrated electric machine (EM) for a hybrid drive of a motor vehicle, comprising a drive shaft ( 1 ), an output shaft ( 2 ) and three planetary gear sets (RS1, RS2, RS3) designed as minus planetary gear sets, which are arranged in a housing (G), six rotatable shafts (FIG. 1 . 2 . 3 . 4 . 5 . 6 ) as well as five switching elements ( 04 . 15 . 26 . 36 . 46 . 35 . 56 ), comprising a brake ( 04 ) and couplings ( 15 . 26 . 36 . 46 . 35 . 56 ), whose selective engagement different transmission ratios between the drive shaft ( 1 ) and the output shaft ( 2 ), wherein the sun gear of a first planetary gear set (RS1) with a fourth wave ( 4 ), which is connected via the brake ( 04 ) can be coupled to the housing (G) and via a fourth coupling ( 46 ) with a sixth wave ( 6 ) is detachably connectable, which rotatably connected to the ring gear of a second planetary gear set (RS2) and via a second clutch ( 26 ) with the output shaft ( 2 ) is detachably connectable, which is rotatably connected to the web of a third planetary gear set (RS3) and the ring gear of the first planetary gear set (RS1), wherein the sixth wave ( 6 ) is rotatably connected or operatively connected to the rotor of an electric machine (EM) and a third shaft ( 3 ) is rotatably connected to the web of the second planetary gear set (RS2) and the ring gear of the third planetary gear set (RS3), wherein the drive shaft ( 1 ) of the transmission with the web of the first planetary gear set (RS1) rotatably connected and via a first clutch ( 15 ) with a with the ring gear of the second planetary gear set (RS2) rotatably connected fifth wave ( 5 ) is detachably connectable, wherein the sun gear of the third planetary gear set (RS3) is coupled to the housing (G) (shaft 0 ) and wherein a third clutch ( 36 . 35 . 56 ) is provided by the closing of the second planetary gear set (RS2) is blockable. Power-shiftable multi-speed transmission according to claim 1, characterized in that a further brake ( 06 ) is provided, by closing the sixth wave ( 6 ) of the transmission to the housing (G) can be coupled. Power-shiftable multistage transmission according to claim 1 or 2, characterized in that the third clutch as a clutch ( 36 ), which is the sixth wave ( 6 ) with the third wave ( 3 ) and thus the ring gear with the web of the second planetary gear set (RS2) releasably connects or as a clutch ( 56 ), which is the sixth wave ( 6 ) with the fifth wave ( 5 ) and thus the ring gear with the sun gear of the second planetary gear set (RS2) releasably connects or as a clutch ( 35 ) which is the third wave ( 3 ) with the fifth wave ( 5 ) and thus releasably connects the web with the sun gear of the second planetary gear set (RS2). Power-shiftable multi-speed transmission according to claim 1, 2 or 3, characterized in that the planetary gear sets (RS1, RS2, RS3) are designed as negative planetary gear sets. Power-shiftable multi-speed transmission according to claim 4, characterized in that at least one planetary gear set is designed as a plus planetary gear, wherein the web and Hohlradanbindung of the planetary gear set designed as plus planetary gear compared to the execution as a minus planetary gear and exchanged the amount of stationary gear ratio by 1 is increased. Power-shiftable multi-speed transmission according to claim 1, 2, 3, 4 or 5, characterized in that the planetary gear seen axially in the order of first planetary gear set (RS1), second planetary gear set (RS2), third planetary gear set (RS3) or in the order third planetary gear set (RS3 ), first planetary gear set (RS1), second planetary gear set (RS2) are arranged. Power-shiftable multi-speed transmission according to one of the preceding claims, characterized in that the switching elements of the transmission are designed as positive-locking switching elements. Power-shiftable multi-speed transmission according to claim 7, characterized in that in each case two switching elements are combined in a double switching element, when these switching elements have a common shaft and do not have to be switched simultaneously in one of the gears. Power-shiftable multi-speed transmission according to claim 1, characterized in that five mechanical forward gears and two electric motor driven forward gears are feasible, wherein the five forward mechanical gears form the forward gears 2-6 of the transmission, wherein the first forward gear of the transmission by closing the first clutch ( 15 ) is switched via an EDA interconnection, wherein the second forward gear by closing the first and the second clutch ( 15 . 26 ), the third forward gear by closing the first clutch ( 15 ) and the third clutch ( 36 - 1 . 56 - 3 . 35 - 4 ), the fourth forward gear by closing the first and fourth clutch ( 15 . 46 ), the fifth forward gear by closing the second and fourth clutch ( 26 . 46 ), the sixth forward gear by closing the brake ( 04 ) and the second clutch ( 26 ), the first electric motor driven forward gear by closing the third clutch ( 36 - 1 . 56 - 3 . 35 - 4 ) and wherein the second electric motor driven forward gear by closing the second clutch ( 26 ), wherein the circuits from the second to the third forward gear with closed first clutch ( 15 ), from the third to the fourth forward gear with the first clutch closed ( 15 ) and from the fourth to the fifth forward gear when the fourth clutch is closed ( 46 ) as electrodynamic circuits (EDS) are executable and wherein the circuit from the fifth to the sixth forward gear driven by the electric machine (EM) with closed second clutch ( 26 ) he follows. Power-shiftable multi-speed transmission according to claim 2, characterized in that six mechanical forward gears and two electric motor driven forward gears are feasible, wherein the six forward mechanical gears form the forward gears 1-6 of the transmission, wherein the first forward gear of the transmission by closing the first clutch ( 15 ) and the further brake ( 06 ), the second forward gear by closing the first and the second clutch ( 15 . 26 ), the third forward gear by closing the first clutch ( 15 ) and the third clutch ( 36 - 1 . 56 - 3 . 35 - 4 ), the fourth forward gear by closing the first and fourth clutch ( 15 . 46 ), the fifth forward gear by closing the second and fourth clutch ( 26 . 46 ), the sixth forward gear by closing the brake ( 04 ) and the second clutch ( 26 ), the first electric motor driven forward gear by closing the third clutch ( 36 - 1 . 56 - 3 . 35 - 4 ) and wherein the second electric motor driven forward gear by closing the second clutch ( 26 ), wherein the circuits from the first to the second forward gear with closed first clutch ( 15 ), from the second to the third forward gear with the first clutch closed ( 15 ), from the third to the fourth forward gear with the first clutch closed ( 15 ) and from the fourth to the fifth forward gear when the fourth clutch is closed ( 46 ) as electrodynamic circuits (EDS) are executable and wherein the circuit from the fifth to the sixth forward gear driven by the electric machine (EM) with closed second clutch ( 26 ) he follows. Power-shiftable multistage transmission according to claim 9 or 10, characterized in that in the first electric motor-driven forward gear, an addition of the internal combustion engine while maintaining the tensile force by closing the first clutch ( 15 ) is feasible, wherein the third forward gear is obtained and that in the second electric motor-driven forward gear, an addition of the internal combustion engine while maintaining the tensile force in the second forward gear by closing the first clutch ( 15 ), in the fifth forward gear by closing the fourth clutch ( 46 ) and in the sixth forward by closing the brake ( 04 ) is feasible. Power-shiftable multistage transmission according to claim 9, characterized in that in EDA operation by closing the first clutch ( 15 ) A ride to the second, third, or fourth forward gear is possible, which ends by closing the further, the respective gear associated switching element of the EDA operation and the corresponding forward gear of the transmission is switched. Power-shiftable multistage transmission according to claim 10, characterized in that in EDA operation by closing the first clutch ( 15 ) A ride to the first, second, third, or fourth forward gear is possible, which closes by closing the further, the respective gear associated switching element of the EDA operation and the corresponding forward gear of the transmission is switched.

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