DE102011089710A1 - Hybrid drive unit of motor car, has spur gear for switchable connection of input shaft to output shaft that is provided with arrangement of idle gears and associated gear-shift element on output shaft - Google Patents

Abstract

A spur gear (Z1) for switchable connection of input shaft (GE2) to output shaft (GA1) is provided with arrangement of idle gear (z21) and associated gear shifting element (C) on output shaft. A spur gear (Z2) for switchable connection of input shaft (GE1) to output shaft (GA1) is provided with arrangement of idle gear (z12) and associated gear-shifting element (A) on input shaft (GE1). The spur gear (Z3) for switchable connection of input shaft (GE2) to output shaft (GA2) is provided with arrangement of idle gears (z33) and associated shift element (D) on output shaft.

Description

The invention relates to a hybrid drive of a motor vehicle, comprising an internal combustion engine with a drive shaft, an operable as a motor and a generator electric machine with a rotor, and a multi-stage transmission with two input shafts and at least one axially parallel to the input shafts arranged output shaft, wherein the first input shaft the drive shaft of the internal combustion engine is connected or connectable, the second input shaft is in driving connection with the rotor of the electric machine, and wherein both input shafts are arranged coaxially and axially adjacent to each other, in each case at least one switchable spur gear can be brought into drive connection with an output shaft, and via an engageable and disengageable coupling switching element rotatably connected to each other.

Hybrid drives with a two input-side transmission shafts and a common output shaft having transmission, in which the first transmission shaft z. B. is connectable via a controllable friction clutch with the drive shaft of an internal combustion engine, the second transmission shaft with the rotor of an electric machine in drive connection, and both transmission shafts selectively over a plurality of switchable spur gears with different translation selectively with the output shaft in drive connection brought about an engageable and disengageable Coupling switching element coupled to each other or can be brought into drive connection, are known in different construction.

So z. B. in the DE 199 60 621 A1 various embodiments of such a hybrid drive described, in which two axially parallel or coaxially arranged countershafts are each selectively connectable via a plurality of switchable spur gears with different gear ratio with a common output shaft in drive connection can be brought. The first countershaft is in each case via a first input constant with an input shaft in drive connection, which is connectable via a controllable friction clutch with the drive shaft of an internal combustion engine. The second countershaft is either directly rotatably connected to the rotor of an electric machine or is connected via a second input constant with the rotor of the electric machine in drive connection. In addition, each one engageable and disengageable coupling switching element is provided, via which the second countershaft via the second input constant to the input shaft in drive connection can be brought or the rotor of the electric machine with the input shaft can be coupled. When the coupling switching element is engaged, the two countershafts are thus also in driving connection with each other via the two input constants.

In another such hybrid drive according to the WO 2008/138 387 A1 are two axially parallel to each other arranged input shafts selectively via a plurality of switchable spur gears with different translation selectively with a common output shaft in drive connection brought. The first input shaft is connectable via a friction clutch with the drive shaft of an internal combustion engine, whereas the second input shaft is directly connected in a rotationally fixed manner to the rotor of an electric machine. The spur gears of both input shafts are arranged in pairs in common radial gear levels and each use a common, arranged on the output shaft output gear. The formation of two axially adjacent output gears as idler gears ensures that the two input shafts can be brought into drive connection with one another via two coupled spur gear stages without the switching of one of the two respective spur gear stages.

Due to the many spur gear stages and the coupling capability of the two countershaft or input shafts, a plurality of gears are available in the aforementioned hybrid drives in all operating modes. Because of the consequent high number of gear levels, however, these known hybrid drives on an unfavorably large axial length, which prevents their use in a front / transverse arrangement in smaller vehicles or at least difficult.

In contrast, the present invention is based on a type of such a hybrid drive, in which the two input shafts coaxially and axially adjacent to each other as well as an engageable and disengageable coupling switching element directly rotatably connected to each other. The first input shaft is connected directly to the drive shaft of the engine or z. B. connectable via a controllable friction clutch with this, whereas the second input shaft is in driving connection with the rotor of the electric machine. Both input shafts can be brought into drive connection via at least one shiftable spur gear stage with the output shaft arranged axially parallel.

Such a hybrid drive, for example, from the unpublished DE 10 2010 030 573 A1 known. In a particularly suitable for the front / transverse installation embodiment of this known hybrid drive after the local there 18 is connectable via a controllable friction clutch with the drive shaft of the internal combustion engine first input shaft via a single switchable spur gear with the axis-parallel arranged output shaft connectable. In contrast, with the rotor of an electric machine rotatably connected second input shaft via two switchable spur gears connectable to the output shaft. The ratios of the three spur gear stages are chosen such that the first gear and the third gear are formed by the two spur gear sets of the second input shaft and the second gear by the spur gear of the first input shaft. While the idler gears and the gear shift elements of the two input shaft associated spur gear arranged on the output shaft and the respective gear shift elements are combined in a common shift package, the idler gear and the gear shift element of the only one of the first input shaft associated spur gear on the first Arranged input shaft and the relevant gear-switching element combined with the coupling switching element in a common switching package. Thus, in this known hybrid drive for the combustion driving and the hybrid driving three gears and for the electric driving two gears available. The reverse gear is generated purely electric motor in this hybrid drive, therefore realized in the electric driving by reversing the direction of rotation of the electric machine.

The present invention has for its object to propose an alternative hybrid drive of the aforementioned type, which provides at least two courses for the electric driving and at least three gears for the combustion driving, having axially short dimensions and thus suitable for a front / transverse installation in a motor vehicle is, which is power shiftable at least in hybrid driving, and allows the charge of an electric energy storage device.

To achieve this object, the hybrid drive with the features of the preamble of claim 1 is characterized by the following additional features: two axially parallel to the two input shafts GE1, GE2 arranged output shafts GA1, GA2, each via an output constant KA1, KA2 with a common output element in drive connection stand, a single second spur gear Z2 for the switchable connection of the first input shaft GE1 with the first output shaft GA1 with an arrangement of the idler gear and the associated gear shift element A on the first input shaft GE1, a summary of the gear shift element A of the second spur gear Z2 of the first Input shaft GE1 and the coupling switching element B in a double switching element S1, a first spur gear Z1 for the switchable connection of the second input shaft GE2 with the first output shaft GA1 with an arrangement of the idler gear and the associated gear shift element C on the first output shaft GA1, and a third spur gear Z3 for the switchable connection of the second input shaft GE2 with the second output shaft GA2 with an arrangement of the idler gear and the associated gear shift element D on the second output shaft GA2.

Advantageous embodiments and further developments of the hybrid drive according to the invention are the subject of the dependent claims.

The invention is therefore based on a known hybrid drive of a motor vehicle, an internal combustion engine VM with a drive shaft, an operable as a motor and generator electric machine EM1, EM1 'with a rotor, and a multi-stage transmission with two input shafts GE1, GE2 and at least an output shaft GA1, GA2 arranged axially parallel to the input shafts GE1, GE2. The first input shaft GE1 is connected to the drive shaft of the internal combustion engine VM or, for example via a clutch K1 connected to this. The second input shaft GE2 is in drive connection with the rotor of the electric machine EM1, EM1 '. Both input shafts GE1, GE2 are arranged coaxially and axially adjacent to each other, in each case via at least one switchable spur gear Z1, Z2, Z3 with an output shaft (GA1, GA2) in drive connection, and rotatably connected via an engageable and disengageable coupling switching element B connected. Such a hybrid drive, for example, from the unpublished DE 10 2010 030 573 A1 the applicant according to the local 18 known.

As in this known hybrid drive, even in the hybrid drive according to the invention, only a single spur gear Z2 is provided for the switchable connection of the first input shaft GE1 with an output shaft GA1, wherein the respective idler gear and the associated gear shift element A are also arranged on the first input shaft GE1 , and the gear shift element A of this spur gear Z2 is combined with the coupling switching element B in a double switching element S1.

Likewise, in the hybrid drive according to the invention as in the known hybrid drive two spur gears Z1, Z3 provided for switchable connection of the second input shaft GE2 with an output shaft, wherein the respective idler gears and the associated gear shift elements C, D are arranged on an output shaft. In contrast to the known hybrid drive, in the hybrid drive according to the invention, however, two output shafts GA1, GA2 arranged axially parallel to the input shafts GE1, GE2 are provided which each have an output constant KA1, KA2 with a common output element, e.g. an axle differential, in drive connection.

While the first output shaft GA1 via the associated second spur gear Z2 with the first input shaft GE1 and via the first spur gear Z1 with the second input shaft GE2 can be brought into drive connection, the second output shaft GA2 via the third spur Z3 only with the second input shaft GE2 in drive connection to be brought. Due to the arrangement of the respective idler gears and the associated gear shift elements C, D on the respective other output shaft GA1, GA2 they can not be summarized as in the known hybrid drive in a double switching element. The functionality of the hybrid drive according to the invention, however, largely corresponds to that of the known hybrid drive.

Due to the possibility of being able to simultaneously engage the two gear shifting elements C, D of the first and third spur gears Z1, Z3 of the second input shaft GE2, the hybrid drive according to the invention additionally has a parking lock function by blocking the transmission that can be achieved in this way. By a suitable design and arrangement of the first and third spur gear Z1, Z3 can also be achieved compared to the known hybrid drive, a reduction of the axial length of the gearbox, so that the hybrid drive according to the invention is also suitable for small vehicles for front / transverse installation.

The two spur gears Z1, Z3 of the second input shaft GE2 can be arranged in a manner known per se in axially adjacent gearwheel planes and each have its own fixed gear. Since the associated gear shift elements C, D are presently designed as individual shift elements, the axial distance between the two spur gears Z1, Z3, which is caused by a double shift element, is eliminated compared to the known hybrid drive. Thus, the two spur gears Z1, Z3 of the second input shaft GE2 can be arranged axially staggered axially to achieve a small axial length of the gearbox.

Alternatively, the two spur gears Z1, Z3 of the second input shaft GE2 to achieve a small axial length of the gearbox can also be arranged in a common gear level and have a common fixed wheel.

To avoid large speed jumps in load circuits, the translations i _Z1 , i _Z2 , i _{Z3 of} the three spur gears Z1, Z2, Z3 are preferably selected such that the translation i _{Z2 of} the single spur gear Z2 of the first input shaft GE1 largely centered between the translations i _Z1 , i _{Z3 of} the two spur gears Z1, Z3 of the second input shaft GE2 is located.

In order to accomplish the actuation of the switching elements C, D of the first and third spur gear Z1, Z3 on the second input shaft GE2 as in a summary in a double switching element with only one switch actuator, these can advantageously via a common shift drum with at least four switching positions P1, P2, P3, P4 be switchable. In this case, both gear shift elements C, D are closed in a first shift position P1, only one of the two gear shift elements (C or D) is closed in two further shift positions P2, P4, and in a further shift position P3 both gear shift elements C, D open. In the former shift position P1, the two speed shift elements C, D are closed in a parking lock function. In the two next-mentioned switching positions P2, P4 one of the two gear shift elements C, D for the circuit of the relevant spur gear Z1, Z3 is closed in each case. In the latter shift position P3, the two gear shift elements C, D are opened, wherein the gear shift element A of the spur gear Z2 of the first input shaft GE1 and the coupling switching element B can be opened or closed, respectively.

In order to prevent or at least mitigate the inevitably occurring rotational irregularities in a combustion engine normally designed as a combustion engine VM of the transmission is preferably provided that the drive shaft of the engine VM is provided with a torsional vibration damper TD or via a torsional vibration damper TD with the first input shaft GE1 of the gearbox in drive connection stands.

In order to expand the hybrid drive according to the invention for combustion and hybrid driving space-saving by further translation stages, it is advantageously provided that the drive shaft of the engine VM via a coaxially arranged over the first input shaft GE1 or the drive shaft and summarized in a second double switching element S2 gear Switching elements E, F two-stage switchable planetary gear PG1, PG1 'with a non-rotatably connected to the drive shaft input element, via the gear shift elements E, F of the second double switching element S2 alternately with another element of the planetary gear PG1, PG1', for example, the drive shaft 2 connectable or fixed to the housing fixed intermediate element, and a rotatably connected to the first input shaft GE1 output element with the first input shaft GE1 is connectable.

Characterized in that the internal combustion engine VM, the two-stage switchable planetary gear PG1, PG1 'is downstream driven, the engine VM can alternately in two Translation stages brought into drive connection with the first input shaft GE1 and, if the second double switching element S2 has a neutral position in which the planetary gear PG1, PG1 'is open, are also decoupled from this first input shaft. Thus, a maximum of six gear ratios are available for the combustion driving operation in conjunction with the as needed closed coupling switching element B.

The planetary gear PG1 is preferably formed as a simple planetary gear set with a sun gear, a planetary carrier carrying a plurality of planet gears and a ring gear. Here, the planet carrier rotatably connected to the drive shaft of the engine VM input element connected, the sun gear via the second double switching element S2 switchable intermediate element, and the ring gear rotatably connected to the first input shaft GE1 output member. With the stand ratio i ₀₁ , in this embodiment of the planetary gear PG1, the translations i _{PG1 of} the planetary gearing PG1 of i _PG1 = 1 and i _PG1 = 1 / (1-1 / i ₀₁ ) which can alternatively be switched via the second double _{shift element} S2 result Connection with the translations i _Z1 , i _Z2 , i _{Z3 of} the three spur gears Z1, Z2, Z3 the six possible translations between the drive shaft of the engine VM and the two output shafts GA1, GA2 result.

Alternatively, the planetary gear PG1 'may also be formed as a simple planetary gear with a sun gear, a planetary carrier supporting a planet carrier and a ring gear, wherein the planet carrier rotatably connected to the drive shaft of the engine VM input element, the ring gear via the second double switching element S2 switchable intermediate element, and the sun gear rotatably connected to the first input shaft GE1 connected output element. With the stand ratio i ₀₁ result in this embodiment of the planetary gear PG1 'thus on the second double switching element S2 alternatively switchable translations of the planetary gear PG1' of i _PG1 = 1 and i _PG1 = 1 / (1 - i ₀₁ ), in conjunction with the translations i _Z1 , i _Z2 , i _{Z3 of} the three spur gears Z1, Z2, Z3 the six possible translations between the drive shaft of the engine VM and the two output shafts GA1, GA2 result.

In order to avoid large speed jumps in load circuits, the ratios i _Z1 , i _Z2 , i _Z3 , i _{01 of} the three spur gears Z1, Z2, Z3 and the planetary gear PG1, PG1 'preferably chosen such that the two via the planetary gear PG1, PG1 'and the spur gear Z2 of the first input shaft GE1 switchable translations between the four on the planetary gear PG1, PG1' and / or the two spur gears Z1, Z3 of the second input shaft GE2 switchable translations are.

To improve the operating characteristics of the hybrid drive according to the invention, it is preferably provided that the drive shaft of the internal combustion engine VM or the first input shaft GE1 is in drive connection with the rotor of a second electric machine EM2, EM2 '. In a technical connection of the second electric machine EM2, EM2 'to the drive shaft of the internal combustion engine VM is a crankshaft starter-generator (KSG,) in a technical connection to the first input shaft GE1 to a so-called integrated starter generator (ISG ). With the second electric machine EM2, EM2 ', among other things, a serial hybrid driving operation is possible in which the second electric machine EM2, EM2' is driven when switched to the neutral position first double switching element S1 as a generator of the engine VM and the electrical energy for driving the first electric machine EM1, EM1 'supplies.

In a standard configuration and arrangement of the second electric machine EM2, this is arranged coaxially over the drive shaft of the internal combustion engine VM and / or the first input shaft GE1, and the rotor of the second electric machine EM2 is directly connected in a rotationally fixed manner to the drive shaft or the first input shaft GE1.

In this standard connection of the second electric machine EM2, it is possible to arrange the planetary gear PG1, PG1 'space-saving axially and radially at least partially within the second electric machine EM2.

As an alternative to the aforementioned standard arrangement, the second electric machine EM2 'can also be arranged parallel to the axis next to the drive shaft of the internal combustion engine VM and / or the first input shaft GE1. In this case, the rotor of the second electric machine EM2 'is in drive connection via a second input constant KE2 designed as a reduction stage with the drive shaft of the internal combustion engine VM or the first input shaft GE1. In this case, the second electric machine EM2 'be formed fast-rotating and relatively weak torque, which is advantageously connected to a particularly compact and lightweight design of the second electric machine EM2'.

In particular, in order to be able to use the second electric machine EM2, EM2 more diversely in an industrial connection to the first input shaft GE1, it is preferably provided that the drive shaft of the internal combustion engine VM via a separating clutch K1 with the first Input shaft GE1 of the gearbox is connectable. As a result, the second electric machine EM2, EM2 'z. B. in electric vehicle operation, ie in uncoupled engine VM, are used as a boost drive and load transfer in load circuits. The separating clutch K1 can be configured both as a friction clutch and as an unsynchronized jaw clutch.

The first electric machine EM1 can also be arranged coaxially over the second input shaft GE2 in a manner known per se, the rotor of this first electric machine EM1 being connected directly to the second input shaft GE2 in a rotationally fixed manner.

As an alternative to this standard arrangement, however, it is also possible for the first electric machine EM1 to be arranged coaxially over the second input shaft GE2, the rotor of this first electric machine EM1 being in drive connection with the second input shaft GE2 via a reduction stage, which is referred to as a second planetary gear PG2 a rotatably connected to the rotor of the first electric machine EM1 input element, a housing fixedly locked intermediate element, and a rotatably connected to the second input shaft GE2 output element is formed. By means of the reduction stage, the rotational speed of the rotor of the first electric machine EM1 is advantageously reduced and the torque of the first electric machine EM1 increased in the same ratio, so that the first electric machine EM1 can be designed to be fast-rotating and relatively weak in torque and thus particularly compact and lightweight.

The second planetary gear PG2 is preferably formed as a simple planetary gear with a sun gear, a planetary carrier supporting a planet carrier and a ring gear, wherein the ring gear rotatably connected to the rotor of the first electric machine EM1 input element, the sun gear fixed to the housing intermediate member, and the planet carrier the non-rotatably connected to the second input shaft GE2 output member forms. With the stand ratio i ₀₂ , the ratio i _{PG2 of} the second planetary gear PG2 to i _PG2 = (1 - 1 / i ₀₂ ).

In an alternative technical connection of the two spur gears Z1, Z3 of the second input shaft GE2 and the first electric machine EM1 is provided that the first electric machine EM1 is indeed arranged coaxially over the second input shaft GE2, but that one coaxial and rotatable on the second input shaft GE2 arranged hollow shaft is provided, on which the fixed gear or the fixed gears of the two Stirnradstufen Z1, Z3 of the second input shaft GE2 is rotationally fixed or are, and which is non-rotatably connected to the rotor of the first electric machine EM1. It is further provided that the second input shaft GE2 is in drive connection with the hollow shaft via a reduction stage, as a second planetary gear PG2 'with a rotatably connected to the second input shaft GE2 input element, a non-rotatable with another element of the planetary gear PG2', for example The input element is connectable and / or fixed to the housing lockable or locked intermediate element, and a rotatably connected to the hollow shaft output element is formed.

With this latter technical connection of the two spur gear Z1, Z3 of the second input shaft GE2 and the first electric machine EM1 is achieved that with closed coupling switching element B and a closed gear shift element (C or D) of the two spur gears Z1, Z3 of second input shaft GE2 different translations i _VM , i _EM1 between the engine VM and the first electric machine EM1 and the respective output shaft (GA1 or GA2) result.

In a non-shiftable embodiment, the second planetary gear PG2 'is preferably formed as a simple planetary gear with a sun gear, a planetary carrier supporting a planet carrier and a ring gear, wherein the planet carrier rotatably connected to the second input shaft GE2 input element, the sun gear locked the housing Intermediate element, and the ring gear rotatably connected to the hollow shaft output member forms. The ratio of the two spur gears Z1, Z3 of the second input shaft GE2 for the internal combustion engine VM is _reduced by the factor i _PG2 = 1 / (1-1 / i ₀₂ ) with the stationary transmission of the second planetary gear PG2 'of i ₀₂ .

In a switchable embodiment, the second planetary gear PG2 'is preferably formed as a simple planetary gear with a sun gear, a planetary carrier supporting a planet carrier and a ring gear, wherein the planet carrier rotatably connected to the second input shaft GE2 input element, the sun gear via the switching elements G. H of a third double switching element S3 alternately rotatably with another element of the planetary gear PG2 ', for example, the planet carrier 20 connectable or fixed to the housing fixed intermediate element, and the ring gear rotatably connected to the hollow shaft output member forms. In this case, the ratio of the two Stirnradstufen Z1, Z3 of the second input shaft GE2 for the engine VM by means of the third double _{switching element} S3 between the factor i _PG2 = 1 and the factor i _PG2 = 1 / (1 - 1 / i ₀₂ ) can be switched ,

In the aforementioned embodiments of the hybrid drive according to the invention with a coaxial arrangement of the first electric machine EM1 on the second input shaft GE2 and a second planetary gear PG2, PG2 ', the respective embodiment of the second planetary gear PG2, PG2' advantageously space-saving axially and radially at least partially within the first electric machine EM1 are arranged.

As an alternative to the aforementioned coaxial arrangements, the electric machine EM1 'can also be arranged parallel to the axis next to the second input shaft GE2, and the rotor of the electric machine EM1' are in drive connection via an input constant KE1 formed as a reduction stage with the second input shaft GE2. With this arrangement, the electric machine EM1 'can be designed to be fast-rotating and relatively weak in torque, which is advantageously connected to a particularly compact and lightweight design of the electric machine EM1'.

According to another drive connection of the internal combustion engine VM and a second electric machine EM2 * to the first input shaft GE1 can be provided that the drive shaft of the engine VM and the rotor of the second electric machine EM2 * are connected via a superposition gear to the first input shaft GE1, wherein the Superposition gear is formed as a simple planetary gear PG1 * with a sun gear, a planet carrier carrying a plurality of planetary gears and a ring gear, which is arranged coaxially over the drive shaft of the engine VM and / or the first input shaft GE1. In this planetary gear PG1 * is the ring gear rotatably connected to the drive shaft first input element, the sun gear rotatably connected to the rotor of the second electric machine EM2 * second input element, and the planet carrier rotatably connected to the first input shaft GE1 output member.

Such a technical connection of an internal combustion engine VM and an electric machine EM2 * to an input shaft GE1 is known from DE 196 50 723 A1 in conjunction with a planetary automatic transmission as well as from the DE 101 52 471 A1 in conjunction with a countershift transmission known as the so-called electrodynamic drive system (EDA) and allows in particular the wear-free starting by means of the internal combustion engine VM by a corresponding control of the electric machine EM2 *.

In order to decouple the internal combustion engine VM in this drive connection of the internal combustion engine VM and the second electric machine EM2 * and still be able to use the second electric machine EM2 * as a drive motor, as a generator and as a synchronization means, it is preferably provided that the drive shaft of the internal combustion engine VM by means of a separating clutch K1 'of the ring gear of the planetary gear PG1 * can be decoupled, and that the sun gear of the planetary gear PG1 * by means of a lock-up clutch K2 rotatably connected to the planet carrier or the first input shaft GE1 is connectable.

In further alternative embodiments, the respective planetary gear PG1, PG1 ', PG1 *, PG2, PG2' could also be designed as a so-called plus gear, e.g. in the design of a double pinion planetary gear, which would require corresponding other connection possibilities of the components (sun gear, planet carrier, ring gear).

To clarify the invention, the description is accompanied by a drawing with exemplary embodiments. In these shows

1 a first embodiment of a hybrid drive according to the invention in a schematic representation,

1a an operating and switching diagram of the hybrid drive according to 1 in the form of a table,

1b a shift drum for operating two-speed switching elements of the hybrid drive according to 1 in a schematic representation,

1c a circuit diagram of the shift drum according to 1b in the form of a table,

2 a second embodiment of a hybrid drive according to the invention in a schematic representation,

3 A third embodiment of a trained according to the invention hybrid drive in a schematic representation,

4 A fourth embodiment of a formed according to the invention hybrid drive in a schematic representation,

4a an operating and switching diagram of the hybrid drive according to 4 in the form of a table,

5 A fifth embodiment of a hybrid drive according to the invention in a schematic representation,

5a an operating and switching diagram of the hybrid drive according to 5 in the form of a table,

6 A sixth embodiment of a hybrid drive according to the invention in a schematic representation,

7 A seventh embodiment of a hybrid drive according to the invention in a schematic representation,

8th An eighth embodiment of an inventively designed hybrid drive in a schematic representation,

8a a circuit diagram of the hybrid drive according to 8th in the form of a table,

9 A ninth embodiment of a hybrid drive according to the invention in a schematic representation,

9a a circuit diagram of the hybrid drive according to 9 in the form of a table,

10 a tenth embodiment of a trained according to the invention hybrid drive in a schematic representation, and

11 An eleventh embodiment of a trained according to the invention hybrid drive in a schematic representation.

In 1 is in schematic form to be regarded as a basic version of the first embodiment of the invention designed according to the hybrid drive 1.1 shown. The hybrid drive 1.1 includes an internal combustion engine VM with a drive shaft 2 , Operated as a motor and as a generator electric machine EM1 with a rotor 3 , and a multi-stage manual transmission 4.1 with two input shafts GE1, GE2 and two output shafts GA1, GA2. The shoot shaft 2 of the internal combustion engine VM is connected via a torsional vibration damper TD with the first input shaft GE1 of the gearbox 4.1 in drive connection. The electric machine EM1 is arranged coaxially over the second input shaft GE2, and the rotor 3 the electric machine EM1 is directly rotatably connected to the second input shaft GE2. The two input shafts GE1, GE2 are arranged coaxially and axially adjacent to each other and rotatably connected to each other via an engageable and disengageable coupling switching element B.

The two output shafts GA1, GA2 are arranged axially parallel to the two input shafts GE1, GE2 and each have an associated output constant KA1, KA2 with an axle differential 5 in drive connection. The two output constants KA1, KA2 each consist of two fixed gears z24, z44 or z34, z44 and use a common output gear z44 on the axle differential 5 because they are arranged in a common gear level. Two each with a drive wheel 6a . 6b Axis shafts connected to a drive axle 7a . 7b are non-rotatable, each with a driven wheel of the axle differential 5 connected.

The first input shaft GE1 can be brought into drive connection via a single switchable spur gear Z2 to the first output shaft GA1, wherein the respective idler gear z12 is rotatably mounted on the first input shaft GE1 and rotatably connected thereto via an associated gear shift element A. This spur gear Z2 is also referred to as the second spur gear Z2. The associated fixed gear z22 is rotatably mounted on the first output shaft GA1. The gear shift element A of the spur gear Z2 of the first input shaft GE1 and the coupling switching element B are combined in a common double switching element S1.

The second input shaft GE2 can be brought into drive connection via two switchable spur gear stages Z1, Z3, each having one of the two output shafts GA1, GA2. These two spur gears Z1, Z3 are also referred to as first and third spur gear Z1, Z3. Via the first spur gear Z1, the second input shaft GE2 can be brought into driving connection with the first output shaft GA1, wherein the relevant fixed gear z11 is secured against rotation on the second input shaft GE2, and the associated idler gear z21 is rotatably mounted on the first output shaft GA1 and via a single switching element trained gear shift element C rotatably connected to this.

Via the third spur gear Z3, the second input shaft GE2 can be brought into drive connection with the second output shaft GA2, wherein the relevant fixed gear z13 is secured against rotation on the second input shaft GE2, and the associated idler gear z33 rotatably supported on the second output shaft GA2 and via a single switching element trained gear shift element D rotatably connected to this.

The translations i _Z1 i _Z2 i _Z3 of the three spur gear Z1, Z2, Z3 are selected such that the ratio i _Z2 of the second spur gear Z2 of the first input shaft GE1 approximately centrally between the ratios i _Z1, i _Z3 of the first and third Spur gear Z1, Z3 of the second input shaft GE2 is (i _Z1 > i _Z2 > i _Z3 ). Therefore, the spur gears Z1, Z2, Z3 according to their translation i _Z1 , i _Z2 , i _Z3 referred to as the first, second and third spur gear.

In the embodiment of the hybrid drive 1.1 according to 1 stand for the combustion driving three gear ratios or gears G1, G2, G3 and for the electric driving two Translation levels available. In hybrid driving all circuits are power shiftable, so without interruption of traction possible. In the table of 1a is a corresponding operating and circuit diagram of the hybrid drive 1.1 according to 1 where the ratios _iZ1 , _iZ2 , _{iZ3 of} the three spur gear stages Z1, Z2, Z3 are assumed as examples with _iZ1 = 2.40, _iZ2 = 1.50 and _iZ3 = 1.00.

In the first four lines of the table the 1a are the switching states of the double switching _element S1 and the two individual switching _elements C, D and the resulting translations i _VM , i _EM1 between the engine VM and the electric machine EM1 and the two output shafts GA1, GA2 indicated for the hybrid driving. It also follows that the electric machine EM1 in the second gear G2 (G2 / a, G2 / b) of the internal combustion engine VM can be operated with two different ratios (i _EM1 = 2.40, i _EM1 = 1.00). In the fifth and sixth rows of the table, the switching state of the double switching _element S1 and the two individual switching _elements C, D and the resulting translations i _EM1 for the electric driving operation with the electric machine EM1 is indicated. In the penultimate row of the table, the switching state of the double switching element S1 and the two individual switching elements C, D when starting the engine VM by means of the electric machine EM1 is given. In this switching state, the stand charge of an electrical energy storage by means of a generator in the operation of the engine VM driven electric machine EM1 is possible. In the last line of the table, the switching state of the double switching element S1 and the two individual switching elements C, D is indicated in a parking lock function. Assuming a powerless EM1 machine, the table of the 1a also the switching states of the double switching element S1 and the two individual switching elements C, D and the resulting translations i _{VM are taken} for the combustion driving with the engine VM.

In order to actuate the two individual switching elements C, D by means of a single switch actuator, so to be able to move in and out, can by a rotary drive about its longitudinal axis rotatable shift drum 26 be used in a schematic way in 1b is shown and their wiring diagram in the table of 1c is specified. Accordingly, the shift drum 26 four switching positions P1-P4. In the first shift position P1 both gear shift elements C, D are closed, whereby a parking lock function is realized. In the second shift position P2, only the gear shift element C is closed, and thus the first spur gear Z1 is switched. In the third shift position P3 both gear shift elements C, D are opened. In this case, z. B. by closing the associated gear shift element A, the second spur Z2 be switched or started with closed coupling switching element B of the engine VM by the electric machine EM1 or the stand charge of an electrical energy storage on the generator operated by the engine VM electric machine EM1 , In the fourth shift position P4, only the gear shift element D is closed and thus the third spur gear Z3 connected.

An in 2 schematically illustrated second embodiment of the invention designed hybrid drive 1.2 with a manual transmission 4.2 differs from the first embodiment according to 1 in that the first input shaft GE1 is connected to the rotor 8th a second electric machine EM2 is in drive connection. The second electric machine EM2 is arranged coaxially over the first input shaft GE1, and the rotor 8th the second electric machine EM2 is directly rotatably connected to the first input shaft GE1.

By the second electric machine EM2, a serial hybrid driving operation is possible, in which the second electric machine EM2 is driven when switched to the neutral position double switching element S1 as a generator of the engine VM and provides the electrical energy for driving the first electric machine EM1. Likewise, the internal combustion engine VM can also be started by the second electric machine EM2 during an electric driving operation with the first electric machine EM1. Finally, the internal combustion engine VM can be assisted in synchronizing the switching elements A, B of the double switching element S1 and thus the relevant circuits can be accelerated.

In the 3 schematically illustrated third embodiment of the invention designed hybrid drive 1.3 with a manual transmission 4.3 differs from the second embodiment according to 2 in that the drive shaft 2 of the internal combustion engine VM now via a clutch K1 with the first input shaft GE1 of the gearbox 4.3 is connectable. This is in addition to the characteristics of the hybrid drive 1.2 according to 2 Also, an electric driving with both electric machines EM1, EM2 possible, in which the synchronization of the switching elements A, B of the first double switching element S1 can be done by the second electric machine EM2.

An in 4 schematically illustrated fourth embodiment of the invention designed hybrid drive 1.4 with a manual transmission 4.4 differs from the third embodiment according to 3 in that the drive shaft 2 of the internal combustion engine VM instead of via a separating clutch K1 now via a coaxial over the drive shaft 2 arranged and summarized in two in a second double switching element S2 gear shift elements E, F two-stage switchable planetary gear PG1 with a rotationally fixed to the drive shaft 2 connected input element, one on the gear shift elements E, F of the second double switching element S2 alternately with the drive shaft 2 connectable or fixed to the housing fixed intermediate element, and a rotatably connected to the first input shaft GE1 output element with the first input shaft GE1 is connectable.

In the present case, the planetary gear PG1 as a simple planetary gear with a sun gear 10 , a planetary carrier carrying a plurality of planetary gears 11 and a ring gear 12 trained, in which the planet carrier 11 the rotation with the drive shaft 2 the internal combustion engine VM connected input element, the sun gear 10 the switchable via the second double switching element S2 intermediate element, and the ring gear 12 the non-rotatably connected to the first input shaft GE1 output element forms.

By virtue of the planetary gearbox PG1, which can be shifted in two stages via the second double-shift element S2, the internal combustion engine VM can thus be connected alternately to the first input shaft GE1 in two transmission stages, which at least theoretically doubles the number of gears available in hybrid and internal combustion mode. Likewise, the internal combustion engine VM can be decoupled by the circuit of the second double switching element S2 in its neutral position of the first input shaft GE1.

In the present case, the planetary gear PG1 space-saving axially and radially disposed within the second electric machine EM2, the rotor 8th over the ring gear 12 of the planetary gear PG1 rotatably connected to the first input shaft GE1.

The in this embodiment of the hybrid drive 1.4 in hybrid _drive usable translations i _VM , i _EM1 , i _EM2 between the engine VM, the first electric machine EM1 and the second electric machine EM2 and the two output shafts GA1, GA2 are in the table of the 4a refer to the circuit diagram. In this application example, the gear ratios i _Z1 i _Z2 i _Z3 of the three spur gear Z1, Z2, Z3 and the stationary transmission ratio i ₀₁ of the planetary gear set PG1 way of example with i _Z1 = 2.25, i _Z2 = 1.72, i _Z3 = 1 , 31 and i ₀₁ = -1.40 are assumed.

It can be deduced from this circuit diagram that two different ratios i _EM1 , i _{EM2 of} the two electric machines EM1, EM2 are possible in the third gear G3 (G3 / a, G3 / b). Due to a respective unfavorable ratio i _{EM1 of} the first electric machine EM1, the switching combinations A, D, E and A, C, F are not used in the present case. Assuming the switched to the neutral position N second double switching element S2, the table of 4a also the switching states of the first double switching _element S1 and the two individual _{switching elements} C, D and the resulting translations i _EM1 , i _{EM2 are taken} for the electric _driving with the two electric machines EM1, EM2. Similarly, the table of the 4a assuming powerless switched electric machines EM1, EM2 and the switching states of the two double switching elements S1, S2 and the two individual switching elements C, D and the resulting translations i _{VM are taken} for the Verbrennungsfahrbetrieb with the engine VM.

An in 5 schematically illustrated fifth embodiment of the invention designed hybrid drive 1.5 with a manual transmission 4.5 differs from the third embodiment according to 3 in that the drive shaft 2 of the internal combustion engine VM instead of via a separating clutch K1 now via a coaxial over the drive shaft 2 arranged and summarized in two in a second double switching element S2 gear shift elements E, F two-stage shiftable planetary gear PG1 'with a rotationally fixed to the drive shaft 2 connected input element, one on the gear shift elements E, F of the second double switching element S2 alternately with the drive shaft 2 connectable or fixed to the housing fixed intermediate element, and a rotatably connected to the first input shaft GE1 output element with the first input shaft GE1 is connectable.

Also in this case, the planetary gear PG1 'as a simple planetary gear with a sun gear 13 , a planetary carrier carrying a plurality of planetary gears 14 and a ring gear 15 formed, in which, however, unlike the above-described embodiment according to 4 the planet carrier 14 the rotation with the drive shaft 2 the internal combustion engine VM connected input element, the ring gear 15 the switchable via the second double switching element S2 intermediate element, and the sun gear 13 the non-rotatably connected to the first input shaft GE1 output element forms.

In this application example as well, the internal combustion engine VM can be alternately connected in two ratio stages to the first input shaft GE1 by means of the planetary gear PG1 'which can be shifted in two stages via the second double shift element S2, whereby the number of gears available in hybrid and internal combustion mode at least theoretically doubles. Likewise is the Internal combustion engine VM also by the circuit of the second double switching element S2 in its neutral position from the first input shaft GE1 decoupled.

Also in the present embodiment of the inventively designed hybrid drive 1.5 is the planetary gear PG1 'space-saving axially and radially disposed within the second electric machine EM2, whose rotor 8th is directly rotatably connected to the first input shaft GE1.

The in this embodiment of the hybrid drive 1.5 in hybrid _drive usable translations i _VM , i _EM1 , i _EM2 between the engine VM, the first electric machine EM1 and the second electric machine EM2 and the two output shafts GA1, GA2 are in the table of the 5a refer to the circuit diagram, analogous to that in the table of 4a specified circuit diagram is constructed. In this application example, the gear ratios i _Z1 i _Z2 i _Z3 of the three spur gear Z1, Z2, Z3 and the stationary transmission ratio i ₀₁ of the planetary gear set PG1 'by way of example with i _Z1 = 2.50, i _Z2 = 1.61, i _Z3 = 1.04 and i ₀₁ = -1.40 assumed. It can be deduced from this circuit diagram that two different ratios i _EM1 , i _{EM2 of} the two electric machines EM1, EM2 are possible in the third gear G3 (G3 / a, G3 / b). Due to a respective unfavorable translation i _{EM1 of} the first electric machine EM1, the switching combinations A, D, E and A, C, F are also not used in this case.

An in 6 schematically illustrated sixth embodiment of the invention designed hybrid drive 1.6 with a manual transmission 4.6 differs from the first embodiment according to 1 in that the two spur gear stages Z1, Z3 associated with the second input shaft GE2 are now arranged in a common gear plane and use a common fixed gear z11 ', which is fastened rotationally fixed on the second input shaft GE2. This is compared to the axially staggered arrangement of the two spur gears Z1, Z3 in the embodiment according to 1 the axial length of the gearbox 4.6 further reduced, which is the front / transverse installation of the hybrid drive according to the invention 1.6 facilitated in a motor vehicle.

In the 7 schematically illustrated seventh embodiment of the invention designed hybrid drive 1.7 with a manual transmission 4.7 differs from the first embodiment according to 1 in that the rotor 3 the first electric machine EM1 with the second input shaft GE2 is now in drive connection via a reduction stage, which as a second planetary gear PG2 with a rotationally fixed to the rotor 3 the first electric machine EM1 connected input element, a fixed housing fixed intermediate element, and a rotatably connected to the second input shaft GE2 output element is formed.

In the present case, the second planetary gear PG2 as a simple planetary gear with a sun gear 16 , a planetary carrier carrying a plurality of planetary gears 17 and a ring gear 18 formed, in which the ring gear 18 the non-rotatable with the rotor 3 the first electric machine EM1 connected input element, the sun gear 16 the housing fixed arrested intermediate element, and the planet carrier 17 the non-rotatably connected to the second input shaft GE2 output member forms.

By the second planetary gear PG2, which is also space-saving axially and radially disposed within the first electric machine EM1, the rotational speed of the rotor 3 reduces the first electric machine EM1 and increases the torque of the first electric machine EM1 in the same ratio, so that the first electric machine EM1 can be performed fast-rotating and relatively weak torque and thus very compact and lightweight. With the stand ratio i _{02 of} the second planetary gear PG2, the corresponding factor results from the ratio i _{PG2 of} the second planetary gear PG2 to i _PG2 = (1 - 1 / i ₀₂ ).

An in 8th schematically illustrated eighth embodiment of the invention designed hybrid drive 1.8 with a manual transmission 4.8 differs from the first embodiment according to 1 in that a hollow shaft arranged coaxially and rotatably on the second input shaft GE2 25 is provided, on which the fixed gears z11, z13 of the two of the second input shaft GE2 associated spur gear Z1, Z3 are arranged rotationally fixed, and rotatably connected to the rotor 3 the first electric machine EM1 is connected. In addition, stands in this embodiment of the hybrid drive 1.8 the second input shaft GE2 with the hollow shaft 25 is drivingly connected via a reduction stage, which as a second planetary gear PG2 'with a non-rotatably connected to the second input shaft GE2 input element, a fixed housing fixed intermediate element, and a rotatably with the hollow shaft 25 connected output element is formed.

In the present case, the second planetary gear PG2 'as a simple planetary gear with a sun gear 19 , a planetary carrier carrying a plurality of planetary gears 20 and a ring gear 21 trained, in which the planet carrier 20 the rotatably connected to the second input shaft GE2 input element, the sun gear 19 the housing fixed arrested intermediate element, and the ring gear 21 the non-rotatable with the hollow shaft 25 forms connected output element.

With this technical connection of the two spur gears Z1, Z3 of the second input shaft GE2 and the first electric machine EM1 is achieved that with closed coupling switching element B and a closed gear shift element (C or D) of the two spur gears Z1, Z3 different translations i _VM , i _EM1 between the engine VM and the first electric machine EM1 and the respective output shaft (GA1 or GA2) result. With the state ratio of the second planetary gear PG2 ', for example, i ₀₂ = -3.00 thus results between the second input shaft GE2 and the hollow shaft 25 a ratio i _PG2 of i _PG2 = 1 / (1-1 / i ₀₂ ) = 0.75, with which the ratio (i _Z1 or i _Z3 ) of the respective spur gear stage (Z1 or Z3) for the internal combustion engine VM is to be multiplied ,

In the table of 8a is a corresponding operating and circuit diagram of the hybrid drive 1.8 according to 8th indicated, wherein the translations i _Z1 , i _Z2 , i _{Z3 of} the three spur gears Z1, Z2, Z3 and the stationary ratio i _{02 of} the second planetary gear PG2 'example with i _Z1 = 2.40, i _Z2 = 1.10, i _Z3 = 1.00 and i ₀₂ = -3.00 are assumed. The structure of the operating and wiring diagram of the table 8a corresponds to that of the table of 1a , so that no further explanation is required.

An in 9 schematically illustrated ninth embodiment of the inventively designed hybrid drive 1.9 with a manual transmission 4.9 differs from the eighth embodiment described above according to 8th in that the second planetary gear PG2 'is now formed in two stages switchable. This is achieved by having the sun gear 19 , which forms the intermediate element of the second planetary gear PG2 ', now alternately rotatably with the planet carrier via the switching elements G, H of a third double switching element S3 20 connectable or fixed to the housing can be locked. Thus, the ratio of the two of the second input shaft GE2 associated spur gears Z1, Z3 for the engine VM by means of the third double _{switching element} S3 now between the factor i _PG2 = 1 and the factor i _PG2 = 1 / (1 - 1 / i ₀₂ ) are switched , resulting in at least theoretically two more gear ratios for the hybrid and combustion driving.

In the table of 9a is a corresponding operating and circuit diagram of the hybrid drive 1.9 according to 9 specified, wherein the transmission ratios i _{Z1, Z2} i, i _Z3 of the three spur gear Z1, Z2, Z3, and the stationary gear ₀₂ i of the second planetary gear set PG2 'by way of example with i _Z1 = 2.40, i = 1.50 _{Z2, Z3} = i 1.00 and i ₀₂ = -3.00 are assumed. The structure of the operating and wiring diagram of the table 9a corresponds largely to that of the table of 8a , However, is extended by a column for the switching state of the switching elements G, H of the third double switching element S3. This operating and switching scheme can be seen that in hybrid driving the two gear ratios of the second planetary gear PG2 'in conjunction with the third spur gear Z3 (gear shift element D is closed) compared in the hybrid drive 1.8 of the 8th are used to switch an additional fourth gear G4, but only one gear ratio in conjunction with the first spur gear Z1 (gear shift element C closed) is used.

An in 10 schematically illustrated tenth embodiment of the invention designed hybrid drive 1.10 with a manual transmission 4.10 differs from the first embodiment according to 1 in that the drive shaft 2 of the internal combustion engine VM and the rotor 9 a second electric machine EM2 * are connected via a superposition gear to the first input shaft GE1, wherein the superposition gear as a simple planetary gear PG1 * with a sun gear 22 , a planetary carrier carrying a plurality of planetary gears and a ring gear 24 is formed, which is arranged coaxially over the first input shaft GE1, and the ring gear 24 the rotation with the drive shaft 2 connected first input element whose sun gear 22 the non-rotatable with the rotor 9 the second electric machine EM2 * connected second input element, and its planet carrier 23 the non-rotatably connected to the first input shaft GE1 output element forms.

The planetary gear PG1 * forms in conjunction with the second electric machine EM2 * a between the drive shaft 2 the internal combustion engine VM and the first input shaft GE1 arranged Vorschaltgetriebe over which the ratio between the engine VM and the first input shaft GE1 is infinitely adjustable. In this way, in particular a wear-free starting by means of the internal combustion engine VM is possible, in which the second electric machine EM2 * is continuously controlled with increasing torque from the generator operation in the engine operation.

In order to decouple the internal combustion engine VM in this technical connection of the internal combustion engine VM and the second electric machine EM2 * and still be able to use the second electric machine EM2 * as a drive motor, as a generator and as a synchronization means, the drive shaft of the engine VM by means of a separating clutch K1 'of the ring gear 24 of Planetary gear PG1 * decoupled, and the sun gear 22 of the planetary gear PG1 * by means of a lock-up clutch K2 rotatably connected to the first input shaft GE1 connectable.

In an in 11 schematically illustrated eleventh embodiment of the invention designed hybrid drive 1.11 with a manual transmission 4.11 is exemplary based on the correspondingly modified second embodiment of the hybrid drive 1.2 according to 2 illustrates that the first electric machine EM1 'and / or the second electric machine EM2' in all the above-described embodiments of the hybrid drive 1.1 - 1.10 Also arranged axially parallel next to the associated input shaft GE1, GE2 and the rotor 3 ' . 8th' the electric machine EM1 ', EM2' in each case via a trained as a reduction stage input constant KE1, KE2 with the relevant input shaft GE1, GE2 or the hollow shaft 25 can be in drive connection. As a result, the respective electric machine EM1 ', EM2' can be designed to be fast-rotating and relatively weak in torque, which is advantageously connected to a particularly compact and lightweight design of the respective electric machine EM1 ', EM2'. It is self-evident that the ratio i _EM1 , i _{EM2 of} an electromechanical machine EM1 ', EM2' connected in such a way with respect to a direct connection to the associated input shaft GE1, GE2 or hollow shaft 25 increased by the factor of the translation i _KE1 , i _KE2 the relevant input constant KE1, KE2.

LIST OF REFERENCE NUMBERS

1.1-1.11

hybrid drive

2

Drive shaft of the internal combustion engine

3, 3 '

Rotor of electric machine EM1, EM1 '

4.1-4.11

manual transmission

5

Axle differential, output element

6a, 6b

drive wheel

7a, 7b

axle shaft

8, 8 '

Rotor of electric machine EM2, EM2 '

9

Rotor of electric machine EM2 *

10

Sun gear of planetary gear PG1

11

Planet carrier of planetary gear PG1

12

Ring gear of planetary gear PG1

13

Sun gear of planetary gear PG1 '

14

Planet carrier of planetary gear PG1 '

15

Ring gear of planetary gear PG1 '

16

Sun gear of planetary gear PG2

17

Planet carrier of planetary gear PG2

18

Ring gear of planetary gear PG2

19

Sun gear of planetary gear PG2 '

20

Planet carrier of planetary gear PG2 '

21

Ring gear of planetary gear PG2 '

22

Sun gear of planetary gear PG1 *

23

Planet carrier of planetary gear PG1 *

24

Ring gear of planetary gear PG1 *

25

hollow shaft

26

shift drum

A

Speed switching element

B

Coupling-switching element

C

Gear shift element, single shift element

D

Gear shift element, single shift element

E, F

Speed switching element

EM1, EM1 '

First electric machine

EM2, EM2 '

Second electric machine

EM2 *

Second electric machine

G _VM

Gear from VM

G1-G5

corridor

GA1

First output shaft

GA2

Second output shaft

GE1

First input shaft

GE2

Second input shaft

i ₀₁

Stand translation of planetary gear PG1, PG1 '

i ₀₂

Stand translation of planetary gear PG2, PG2 '

i _EM1

Translation between EM1 and GA1, GA2

i _EM2

Translation between EM2 and GA1, GA2

i _KE1

Translation of input constant KE1

i _KE2

Translation of input constant KE2

i _PG1

Translation of planetary gear PG1, PG1 '

i _PG2

Translation of planetary gear PG2, PG2 '

i _VM

Translation between VM and GA1, GA2

i _Z1

Translation of Z1

i _Z2

Translation of Z2

K1, K1 '

separating clutch

K2

lock-up clutch

KA1

First output constant of output shaft GA1

KA2

Second output constant of output shaft GA2

KE1

First input constant (to electric machine EM1 ')

KE2

Second input constant (to electric machine EM2 ')

N

Neutral position (from S1, C, D, S2, S3)

P1-P4

Shift positions of shift drum 26

PG1, PG1 '

First planetary gear

PG 1 *

First planetary gear

PG2, PG2 '

Second planetary gear

S1

First double switching element

S2

Second double switching element

S3

Third double switching element

TD

torsional vibration dampers

VM

internal combustion engine

Z1

First spur gear stage

Z2

Second spur gear

Z3

Third spur gear

z11

Drive wheel, fixed gear from Z1

z11 '

Drive wheel, fixed gear from Z1, Z3

z12

Drive wheel, idler gear from Z2

z13

Drive wheel, fixed gear from Z3

z21

Output gear, idler gear from Z1

z22

Output gear, fixed gear from Z2

z24

Drive wheel, fixed gear from KA1

z33

Output gear, idler gear from Z3

z34

Drive wheel, fixed gear from KA2

Z44

Output gear, fixed gear from KA1, KA2

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 19960621 A1 [0003]
• WO 2008/138387 A1 [0004]
• DE 102010030573 A1 [0007, 0011]
• DE 19650723 A1 [0041]
• DE 10152471 A1 [0041]

Claims (25)

Hybrid drive of a motor vehicle having an internal combustion engine (VM) with a drive shaft ( 2 ), an electric machine (EM1, EM1 ') operable as a motor and as a generator with a rotor ( 3 . 3 ' ), and a multi-stage manual transmission ( 4.1 - 4.11 ) with two input shafts (GE1, GE2) and at least one output shaft (GA1, GA2) arranged parallel to the input shafts (GE1, GE2), the first input shaft (GE1) being connected to the drive shaft (GE1). 2 ) of the internal combustion engine (VM) is connected or connectable, wherein the second input shaft (GE2) with the rotor ( 3 . 3 ' ) of the electric machine (EM1, EM1 ') is in driving connection, and in which both input shafts (GE1, GE2) are arranged coaxially and axially adjacent to each other, in each case via at least one switchable spur gear (Z2, Z1, Z3) with an output shaft (GA1, GA2) can be brought into drive connection, and via an engageable and disengageable coupling switching element (B) rotatably connected to each other, characterized by two axially parallel to the input shafts (GE1, GE2) arranged output shafts (GA1, GA2), each having an output constant ( KA1, KA2) with a common output element ( 5 ) are in driving connection, a single second spur gear (Z2) for the switchable connection of the first input shaft (GE1) with the first output shaft (GA1) with an arrangement of the idler gear (z12) and the associated gear shift element (A) on the first input shaft ( GE1), a summary of the gear shift element (A) of the second spur gear (Z2) of the first input shaft (GE1) and the coupling switching element (B) in a double switching element (S1), a first spur gear (Z1) for the switchable connection of the second Input shaft (GE2) with the first output shaft (GA1) with an arrangement of the idler gear (z21) and the associated gear shift element (C) on the first output shaft (GA1), and a third spur gear (Z3) for the switchable connection of the second input shaft (GE) ( GE2) with the second output shaft (GA2) with an arrangement of the idler gear (z33) and the associated gear shift element (D) on the second output shaft (GA2). Hybrid drive according to Claim 1, characterized in that the spur gear stages (Z1, Z3) of the second input shaft (GE2) are arranged in axially adjacent gearwheel planes and each have their own fixed gear (z11, z31). Hybrid drive according to claim 1, characterized in that the spur gears (Z1, Z3) of the second input shaft (GE2) are arranged in a common gear plane and have a common fixed wheel (z11 '). Hybrid drive according to one of claims 1 to 3, characterized in that the translations (i _Z1 , i _Z2 , i _Z3 ) of the three spur gears (Z1, Z2, Z3) are selected such that the translation (i _Z2 ) of the spur gear (Z2 ) of the first input shaft (GE1) lies substantially in the middle between the translations (i _Z1 , i _Z3 ) of the two spur gear stages (Z1, Z3) of the second input shaft (GE2). Hybrid drive according to one of claims 1 to 4, characterized in that the gear shift elements (C, D) of the two spur gears (Z1, Z3) of the second input shaft (GE2) via a common shift drum ( 26 ) are switchable with at least four switching positions (P1-P4), wherein in a first switching position (P1) both gear shift elements (C, D) are closed, in two other switching positions (P2, P4) in each case only one of the two gear shift elements (C or D) is closed, and in another switching position (P3) both gear shift elements (C, D) are opened. Hybrid drive according to one of claims 1 to 5, characterized in that the drive shaft ( 2 ) of the internal combustion engine (VM) with a torsional vibration damper (TD) or via a torsional vibration damper (TD) with the first input shaft (GE1) of the gearbox ( 4.1 - 4.3 . 4.6 - 4.11 ) is in drive connection. Hybrid drive according to one of claims 1 to 6, characterized in that the drive shaft ( 2 ) of the internal combustion engine (VM) via a coaxial over the first input shaft (GE1) or the drive shaft ( 2 ) arranged and two summarized in a second double switching element (S2) gear shift elements (E, F) two-stage switchable planetary gear (PG1, PG1 ') with a rotationally fixed to the drive shaft ( 2 ) connected input element, one on the gear shift elements (E, F) of the second double switching element (S2) alternately with another element of the planetary gear (PG1, PG1 ') of the drive shaft connectable or fixed to the housing lockable intermediate element, and a rotationally fixed to the first input shaft ( GE1) connected to the first input shaft (GE1) is connectable. Hybrid drive according to claim 7, characterized in that the planetary gear (PG1) as a simple planetary gear with a sun gear ( 10 ), a planet carrier carrying a plurality of planet wheels ( 11 ) and a ring gear ( 12 ) is formed, in which the planet carrier ( 11 ) rotatably with the drive shaft ( 2 ) of the internal combustion engine (VM) connected input element, the sun gear ( 10 ) via the second double switching element (S2) switchable intermediate element, and the ring gear ( 12 ) rotatably connected to the first input shaft (GE1) connected output element. Hybrid drive according to claim 7, characterized in that the planetary gear (PG1 ') as a simple planetary gear with a sun gear ( 13 ), a planet carrier carrying a plurality of planet wheels ( 14 ) and a ring gear ( 15 ) is formed, in which the planet carrier ( 14 ) rotatably with the drive shaft ( 2 ) of the internal combustion engine (VM) connected input element, the ring gear ( 15 ) via the second double switching element (S2) switchable intermediate element, and the sun gear ( 13 ) rotatably connected to the first input shaft (GE1) connected output element. Hybrid drive according to one of claims 7 to 9, characterized in that the translations (i _Z1 , i _Z2 , i _Z3 , i ₀₁ ) of the three spur gears (Z1, Z2, Z3) and the planetary gear (PG1, PG1 ') are selected such in that the two ratios which can be shifted via the planetary gear (PG1, PG1 ') and the spur gear (Z2) of the first input shaft (GE1) are distributed between the four via the planetary gear (PG1, PG1') and / or the two spur gears (Z1, Z3). the second input shaft (GE2) switchable translations lie. Hybrid drive according to one of claims 1 to 10, characterized in that the drive shaft ( 2 ) of the internal combustion engine (VM) or the first input shaft (GE1) with the rotor ( 8th . 8th' ) is in drive connection with a second electric machine (EM2, EM2 '). Hybrid drive according to claim 11, characterized in that the second electric machine (EM2) coaxial with the drive shaft ( 2 ) of the internal combustion engine (VM) and / or the first input shaft (GE1) is arranged, and the rotor ( 8th ) of the second electric machine (EM2) directly against rotation with the drive shaft ( 2 ) or the first input shaft (GE1) is connected. Hybrid drive according to one of claims 7 to 12, characterized in that the planetary gear (PG1, PG1 ') axially and radially at least partially within the second electric machine (EM2) is arranged. Hybrid drive according to one of claims 1 to 11, characterized in that the second electric machine (EM2 ') parallel to the axis next to the drive shaft ( 2 ) of the internal combustion engine (VM) and / or the first input shaft (GE1) is arranged, and the rotor ( 8th' ) of the second electric machine (EM2 ') via a trained as a reduction stage second input constant (KE2) with the drive shaft ( 2 ) of the internal combustion engine (VM) or the first input shaft (GE1) is in drive connection. Hybrid drive according to one of claims 11 to 14, characterized in that the drive shaft ( 2 ) of the internal combustion engine (VM) via a separating clutch (K1) with the first input shaft (GE1) of the gearbox ( 4.3 . 4.10 ) is connectable. Hybrid drive according to one of claims 1 to 15, characterized in that the first electric machine (EM1) is arranged coaxially over the second input shaft (GE2), and the rotor ( 3 ) of the first electric machine (EM1) is directly connected in a rotationally fixed manner to the second input shaft (GE2). Hybrid drive according to one of claims 1 to 15, characterized in that the first electric machine (EM1) is arranged coaxially over the second input shaft (GE2), and the rotor ( 3 ) of the first electric machine (EM1) is in driving connection with the second input shaft (GE2) via a reduction stage, which as a second planetary gear (PG2) with a rotationally fixed to the rotor ( 3 ) of the first electric machine (EM1) connected input element, a fixed housing fixed intermediate element, and a rotatably connected to the second input shaft (GE2) output element is formed. Hybrid drive according to claim 17, characterized in that the second planetary gear (PG2) as a simple planetary gear with a sun gear ( 16 ), a planet carrier carrying a plurality of planet wheels ( 17 ) and a ring gear ( 18 ) is formed, wherein the ring gear ( 18 ) rotatably with the rotor ( 3 ) of the first electric machine (EM1) connected input element, the sun gear ( 16 ) the housing fixed arrested intermediate element, and the planet carrier ( 17 ) rotatably connected to the second input shaft (GE2) connected output element. Hybrid drive according to one of claims 1 to 15, characterized in that the first electric machine (EM1) is arranged coaxially above the second input shaft (GE2) that a coaxially and rotatably mounted on the second input shaft (GE2) hollow shaft ( 25 ) is provided, on which the fixed gear (Z11 ') or the fixed wheels (Z11, Z13) of the two spur gears (Z1, Z3) of the second input shaft (GE2) is rotationally fixed or are, and the rotationally fixed to the rotor ( 3 ) of the first electric machine (EM1) is connected, and that the second input shaft (GE2) with the hollow shaft ( 25 ) is in drive connection via a reduction stage, which as a second planetary gear (PG2 ') with a rotatably connected to the second input shaft (GE2) input element, a non-rotatably connected to another element of the planetary gear (PG2') connectable to the input member and / or fixed to the housing or locked intermediate element, and a non-rotatable with the hollow shaft ( 25 ) connected output element is formed. Hybrid drive according to claim 19, characterized in that the second planetary gear (PG2 ') as a simple planetary gear with a sun gear ( 19 ), a planet carrier carrying a plurality of planet wheels ( 20 ) and a ring gear ( 21 ) is formed, in which the planet carrier ( 20 ) the rotatably connected to the second input shaft (GE2) input element, the sun gear ( 19 ) the housing fixed locked intermediate element, and the ring gear ( 21 ) rotatably with the hollow shaft ( 25 ) connected output element forms. Hybrid drive according to claim 19, characterized in that the second planetary gear (PG2 ') as a simple planetary gear with a sun gear ( 19 ), a planet carrier carrying a plurality of planet wheels ( 20 ) and a ring gear ( 21 ) is formed, in which the planet carrier ( 20 ) the rotatably connected to the second input shaft (GE2) input element, the sun gear ( 19 ) via the switching elements (G, H) of a third double switching element (S3) alternately rotatably with another element of the planetary gear (PG2 ') the planet carrier ( 20 ) connectable or fixed to the housing lockable intermediate element, and the ring gear ( 21 ) rotatably with the hollow shaft ( 25 ) connected output element forms. Hybrid drive according to one of claims 17 to 21, characterized in that the second planetary gear (PG2, PG2 ') axially and radially at least partially within the first electric machine (EM1) is arranged. Hybrid drive according to one of claims 1 to 15, characterized in that the electric machine (EM1 ') is arranged axially parallel next to the second input shaft (GE2), and the rotor ( 3 ' ) of the electric machine (EM1 ') via a formed as a reduction stage input constant (KE1) with the second input shaft (GE2) is drivingly connected. Hybrid drive according to one of claims 1 to 6 and 15 to 23, characterized in that the drive shaft ( 2 ) of the internal combustion engine (VM) and the rotor ( 9 ) of a second electric machine (EM2 *) via a superposition gear to the first input shaft (GE1) are connectable, wherein the superposition gear as a simple planetary gear (PG1 *) with a sun gear ( 22 ), a planet carrier carrying a plurality of planet wheels ( 23 ) and a ring gear ( 24 ) formed coaxially over the drive shaft ( 2 ) of the internal combustion engine (VM) and / or the first input shaft (GE1) is arranged, and whose ring gear ( 24 ) rotatably with the drive shaft ( 2 ) connected first input element whose sun gear ( 22 ) rotatably with the rotor ( 9 ) of the second electric machine (EM2 *) connected second input element, and its planet carrier ( 23 ) rotatably connected to the first input shaft (GE1) connected output element. Hybrid drive according to claim 24, characterized in that the drive shaft ( 2 ) of the internal combustion engine (VM) by means of a separating clutch (K1 ') of the ring gear ( 24 ) of the planetary gear (PG1 *) is decoupled, and that the sun gear ( 22 ) of the planetary gear (PG1 *) by means of a lock-up clutch (K2) rotatably with the planet carrier ( 23 ) or the first input shaft (GE1) is connectable.

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