Hybrid drive device

Abstract

Hybrid drive device comprising an internal combustion engine (10a; 10b), an electric machine (11a; 11b), a planetary gear set (38a; 38b), a first spur gear set (20a; 20b) and a second spur gear set (21a; 21b), wherein the internal combustion engine (10a; 10b) is connected to the planetary gear set (38a; 38b) via a disconnecting clutch (39a; 39b) and the electric machine (11a; 11b) is directly connected to the planetary gear set (38a; 38b), wherein the two spur gear units (20a, 21a; 20b, 21b) are directly connected to the planetary gear set (38a; 38b), wherein the planetary gear set (38a; 38b) comprises a first planetary gear set (41a; 41b) and a second planetary gear set (42a, 42b), wherein the first planetary gear set (41a; 41b) comprises a first ring gear (43a; 43b) and a first sun gear (46a; 46b), wherein at least one web (47a, 48a) of a planetary gear set (44a; 44b; 45a; 45b) of the first planetary gear set (41a; 41b) and at least one web (49a, 49b) of a planetary gear set (51a, 51b) of the second planetary gear set (42a; 42b) are connected to each other in a rotationally fixed manner, wherein the second planetary gear set (42a; 42b) has a second ring gear (50a; 50b), and wherein the second ring gear (50a; 50b) is coupled non-rotatably to a rotor (13a; 13b) of the electric machine (11a; 11b), characterized in that the first planetary gear set (41a; 41b) comprises an outer planetary gear set (44a; 44b) and an inner planetary gear set (45a; 45b), wherein the outer planetary gear set (44a; 44b) and the inner planetary gear set (45a; 45b) form a double planetary gear set with a first and second rib (47a, 48a; 47b, 48b), and in that the second planetary gear set (42a; 42b) comprises the planetary gear set (51a; 51b) of the second planetary gear set (42a; 42b) with a third rib (49a; 49b), wherein the first, second and third ribs (47a, 48a, 49a; 47b, 48b, 49b) are rotationally fixed to one another.

Description

[0001] The invention relates to a hybrid drive device with an internal combustion engine, an electric machine, a planetary gear set, a first spur gear set and a second spur gear set, wherein the internal combustion engine is connected to the planetary gear set via a disconnect clutch and the electric machine is connected directly to the planetary gear set, wherein the two spur gear sets are connected directly to the planetary gear set, wherein the planetary gear set has two planet gear sets, wherein a first planet gear set has a first ring gear, an outer planet set, an inner planet set, and a first sun gear, wherein the outer planet set and the inner planet set form a double planet set with a first and second web.

[0002] From DE 10 2010 053 757 A1, a hybrid drive device is already known, comprising an internal combustion engine, an electric machine, a planetary gear set, a first spur gear set and a second spur gear set, wherein the internal combustion engine is connected to the planetary gear set via a disconnect clutch and the electric machine is directly connected to the planetary gear set, wherein the two spur gear sets are directly connected to the planetary gear set, wherein the planetary gear set has two planet gear sets, wherein a first planet gear set has a first ring gear and a first sun gear, wherein at least one web of a planet gear set of the first planet gear set and at least one web of a planet gear set of the second planet gear set are rotationally fixed to each other.Furthermore, DE 10 2006 050 598 A1 and DE 10 2007 043 173 A1 each disclose a hybrid drive device in which, in addition to the features shown in DE 10 2010 053 757 A1, the second planetary gear set has a second ring gear. WO 2014 / 046 580 A1 discloses a similarly designed hybrid drive device with a planetary gear set and two spur gear sets, wherein the planetary gear set has a brake unit for braking a shaft of the planetary gear set.

[0003] The invention is based in particular on the objective of providing a hybrid drive device with a particularly simple basic design and a particularly high level of shifting comfort. This is achieved by an embodiment according to the invention as defined in claim 1. Further developments of the invention are set forth in the dependent claims.

[0004] The invention relates to a hybrid drive device with an internal combustion engine, an electric machine, a planetary gear set, a first spur gear set and a second spur gear set, wherein the internal combustion engine is connected to the planetary gear set via a disconnect clutch and the electric machine is directly connected to the planetary gear set, wherein the two spur gear sets are directly connected to the planetary gear set, wherein the planetary gear set has two planet gear sets, wherein a first planet gear set has a first ring gear and a first sun gear, wherein at least one web of a planet gear set of the first planet gear set and at least one web of a planet gear set of the second planet gear set are rotationally fixed to each other.

[0005] In a manner known per se, it is further assumed that the second planetary gear set has a second ring gear. This allows for particularly smooth shifting while maintaining a simple design. Furthermore, the hybrid drive system can be advantageously designed to be especially compact. The planetary gear set is specifically intended to combine the drive torques of the combustion engine and the electric motor and transmit them as a single drive torque to a transmission unit. The transmission unit preferably comprises at least the first spur gear unit and the second spur gear unit. "Specifically intended" is understood to mean specifically designed and / or equipped.

[0006] The first spur gear unit is preferably designed for shifting one gear, while a gear is engaged in the second spur gear unit. Preferably, the first and second spur gear units are independent of each other; that is, a second gear can be engaged in the first spur gear unit independently of a gear engaged in the second spur gear unit. A shift logic for the transmission unit comprising the two spur gear units is defined by a load-shift capability between the two spur gear units. Preferably, two spur gear units are connected together, with each spur gear unit forming a portion of the spur gear units. A gear can be formed by either of the two spur gear units or by both spur gear units together.Preferably, the spur gear unit comprises a first and a second input shaft and at least one output shaft. Preferably, at least one coupling-compatible loose gear and one fixed output gear are arranged on the output shaft.

[0007] The second ring gear is coupled to a rotor of the electric machine in a manner known per se. It has been shown that advantageous gear ratios can be achieved through such a coupling.

[0008] According to the invention, the first planetary gear set comprises an outer planetary gear set and an inner planetary gear set, wherein the outer and inner planetary gear sets form a double planetary gear set with a first and second web, and wherein the second planetary gear set comprises the planetary gear set of the second planetary gear set with a third web, the first, second, and third webs being rotationally fixed to one another. This allows the planetary gear sets to be advantageously interconnected in a compact manner. "Connected to one another" is understood to mean, in particular, a form-fit and / or material connection. Preferably, the webs are formed integrally with one another.

[0009] As an advantageous further development of the invention, it is proposed that the second planetary gear set includes a second sun gear. Thus, the planetary gear set is designed as a five-shaft planetary gear set, which allows for particularly smooth shifting.

[0010] Furthermore, it is proposed that the planetary gear set includes a braking unit designed for the direct braking of a planetary gear set shaft. Direct braking means that no additional coupling unit is arranged between the braking unit and the planetary gear set shaft to be braked. A planetary gear set shaft refers to a shaft of a rotatable element of the planetary gear set. Rotatable elements of the planetary gear set include sun gears, ring gears, and planet carriers.

[0011] The ability to brake a shaft of the planetary gear system allows for the advantageous reduction and / or prevention of shift hesitation during gear changes. Furthermore, multiple purely electrically operated power-shift gears can be easily engaged. Additionally, gear ratios are continuously variable, at least in certain ranges. In this context, "braking" refers specifically to a reduction in the rotational speed of the shaft being braked relative to the planetary gear housing. Specifically, the braking unit is designed to completely brake or lock the shaft relative to the gearbox housing.

[0012] Furthermore, it is proposed that the planetary gear set includes a coupling unit designed for a rotationally fixed coupling of two shafts within the planetary gear set. Such a coupling unit allows for the complete locking of the planetary gear set, resulting in a low-loss transmission of gears via the spur gear units. This also enables a particularly high number of selectable gears. "Rotationally fixed coupling" is understood to mean, in particular, that two elements of the planetary gear set are connected to each other by a positive and / or frictional connection and are essentially rigid. The coupling unit is designed to lock the planetary gear set. When the planetary gear set is locked, all planetary gear sets and the ring gears rotate at the same speed.

[0013] Preferably, the first spur gear unit and / or the second spur gear unit comprises at least one switching unit. A "switching unit" is understood to be, in particular, a unit with exactly two coupling elements designed to connect two rotatably mounted gear elements, such as a loose gear and a gear output shaft, a loose gear and a gear input shaft, or adjacent loose gears of different gear planes, in a switchable yet rotationally fixed manner. Two adjacent, particularly axially adjacent, switching units can, in principle, be combined into a common double switching unit, for example, by providing a common coupling element for both switching units.Each of the switching units can basically be designed as a purely positive-locking switching unit, for example as a jaw coupling, as a positive-locking and friction-locking switching unit, for example in the form of a synchronized jaw coupling, or as a purely friction-locking switching unit, for example in the form of a multi-plate clutch.

[0014] Advantageously, a radial distance of an axis of rotation of the planetary set of the second planetary gear set from a central axis of the planetary gear set is smaller than a radial distance of an axis of rotation of the inner planetary set from the central axis of the planetary gear set, and a radial distance of an axis of rotation of the inner planetary set from the central axis is smaller than a radial distance of an axis of rotation of the outer planetary set from the central axis.

[0015] Furthermore, it is proposed that the first sun gear, the double planetary gear set, and the first ring gear be arranged in a first gear plane of the planetary gear set. This allows the planetary gear set to be designed in a particularly compact manner.

[0016] Furthermore, it is proposed that the second planetary gear set includes a second sun gear, with the second sun gear, the planetary gear set of the second planetary gear set, the second ring gear, and the inner planetary gear set being arranged in a second gear plane of the planetary gear set. This allows the planetary gear set to be designed in a particularly compact manner.

[0017] It is further proposed that the first, second, and third webs between the first and second gear planes be rotationally fixed to a partial gear input shaft of the planetary gear set. This allows for a particularly simple and structurally advantageous torque transmission from the gear planes to the partial gear sets. Advantageously, the first partial gear input shaft is designed as a solid shaft. Alternatively, the first partial gear input shaft is designed as a hollow shaft. It is also advantageous for the first partial gear input shaft to be arranged centrally within the planetary gear set when viewed in a radial direction.

[0018] Furthermore, it is proposed that the brake unit be designed to brake the first ring gear. This results in a particularly advantageous arrangement of the brake unit from a design perspective.

[0019] Furthermore, it is proposed that the coupling unit be designed to provide a rotationally fixed coupling between the second ring gear and the second sun gear. This allows for a particularly advantageous arrangement of the coupling unit from a structural point of view.

[0020] Furthermore, it is proposed that the second sun gear be rotationally fixed to a second partial input shaft of the planetary gear set. This allows for a particularly simple and compact design of the hybrid drive device.

[0021] Furthermore, it is proposed that the inner planetary gear set extends into both the first and second gear planes. The inner planetary gear set thus meshes with an element of both the first and second planetary gear sets. This allows both gear planes, or both planetary gear sets, to be easily interconnected, resulting in a particularly high number of selectable gears.

[0022] Furthermore, it is proposed that the first spur gear unit and the second spur gear unit, together with the planetary gear unit, be configured to provide a transmission with at least eleven different gears. This would allow for particularly advantageous driving characteristics. Shifting comfort can also be significantly improved.

[0023] It is further proposed that the partial transmission input shaft be designed as a hollow shaft. This allows the transmission to be designed in a particularly compact manner.

[0024] Furthermore, it is proposed that the combustion engine and the spur gear units are arranged on opposite sides of the planetary gear unit when viewed axially. This allows the hybrid drive unit to be designed in a particularly compact manner. In an alternative embodiment, it is proposed that the combustion engine and the planetary gear unit are arranged on opposite sides of the spur gear unit when viewed axially. This allows the hybrid drive unit to be designed in a particularly compact manner.

[0025] Further advantages will become apparent from the following description of the figures. The figures illustrate two exemplary embodiments of the invention. The figures, the description of the figures, and the claims contain numerous features in combination. A person skilled in the art will expediently consider the features individually and combine them into meaningful further combinations.

[0026] This shows: Fig. 1 a planetary gear of a first embodiment of a hybrid drive device in a schematic representation, Fig. 2 the planetary gear Fig. 1 in a schematic projection representation, Fig. 3 the planetary gear Fig. 1 in a further schematic representation, Fig. 4 the hybrid drive device with the planetary gear and a gear unit in a schematic representation, Fig. 5 a switching table of the hybrid drive device and Fig. 6 Another embodiment of a hybrid drive device in a schematic representation.

[0027] The Fig. 1, Fig. 2 to Fig. Figure 3 shows a schematic representation of a portion of the powertrain of a hybrid vehicle, including a first embodiment of a hybrid drive device according to the invention. The hybrid drive device is designed as a vehicle hybrid drive device. To generate drive torque, the hybrid drive device comprises an internal combustion engine 10a. It is also conceivable, in principle, that instead of the internal combustion engine 10a, another drive motor, which would appear advantageous to a person skilled in the art, is provided.

[0028] To generate additional drive torque, the hybrid drive device includes an electric machine 11a. The electric machine 11a functions as an electric motor. It would also be possible to use a hydraulic or pneumatic drive unit with a corresponding energy storage device instead of the electric machine 11a. The electric machine 11a is designed to convert either electrical energy into mechanical energy or vice versa. For this purpose, the electric machine 11a includes a stator 12a and a rotor 13a. The stator 12a is rigidly connected to a gearbox housing 14a. The gearbox housing 14a is rotationally fixed and rigidly connected to the body of the hybrid vehicle. The rotor 13a is rotatably mounted relative to the stator 12a.For the provision and storage of electrical energy, the hybrid vehicle has a battery device (not shown in detail). The battery device is designed to provide electrical energy for driving the electric machine 11a and to store electrical energy generated by the combustion engine 10a or supplied from an external power grid.

[0029] As in the Fig. As shown in Figure 4, the hybrid drive device for providing multiple gear ratios comprises a transmission unit 15a. To introduce drive torque, the transmission unit 15a has a first partial transmission input shaft 16a and a second partial transmission input shaft 17a. The first partial transmission input shaft 16a is designed as a solid shaft. The second partial transmission input shaft 17a is designed as a hollow shaft. The first partial transmission input shaft 16a and the second partial transmission input shaft 17a are arranged coaxially with each other. The first partial transmission input shaft 16a passes through the second partial transmission input shaft 17a.

[0030] To transmit a drive torque, i.e., an output torque, translated by the transmission unit 15a, the transmission unit 15a has a first transmission output shaft 18a and a second transmission output shaft 19a. The transmission output shafts 18a and 19a are arranged parallel to and offset from the partial transmission input shafts 16a and 17a. The transmission output shafts 18a and 19a are intended for connection to drive wheels of the hybrid vehicle (not shown in detail).

[0031] The gear unit 15a comprises a first spur gear unit 20a and a second spur gear unit 21a. The first spur gear unit 20a and the second spur gear unit 21a can be connected in parallel to each other in a power flow. The first spur gear unit 20a is arranged axially upstream of the second spur gear unit 21a.

[0032] The first spur gear unit 20a has two different gear ratios. The first spur gear unit 20a has the first sub-gearbox input shaft 16a. The drive torque is introduced into the first spur gear unit 20a via the first sub-gearbox input shaft 16a. To set the two different sub-gear ratios, the first spur gear unit 20a has a first gear pair 22a, a second gear pair 23a, a first shift unit 24a, and a second shift unit 25a. The first shift unit 24a is designed as a double shift unit. The first gear pair 22a has a fixed gear 26a mounted on the first sub-gearbox input shaft 16a and a loose gear 27a rotatably mounted on the first gearbox output shaft 18a. The second gear pair 23a has a fixed gear 28a arranged rigidly on the first partial transmission input shaft 16a and a loose gear 29a rotatably arranged on the second transmission output shaft 19a.The loose gears 27a, 29a mesh with the respective fixed gears 26a, 28a. The two switching units 24a, 25a connect the loose gears 27a, 29a to the first transmission output shaft 18a and the second transmission output shaft 19a respectively, preventing rotation of each gear.

[0033] The second spur gear unit 21a has two different gear ratios. The second spur gear unit 21a has a second input shaft 17a. The drive torque is introduced into the second spur gear unit 21a via the second input shaft 17a. To adjust the two different gear ratios, the second spur gear unit 21a has a first gear pair 30a, a second gear pair 31a, a third shift unit 32a, and a fourth shift unit 33a. The third shift unit 32a is designed as a double shift unit together with the first shift unit 24a. The third gear pair 30a has a fixed gear 34a mounted on the second input shaft 17a and a loose gear 35a rotatably mounted on the first output shaft 18a.The fourth gear pair 31a comprises a fixed gear 36a mounted on the second partial transmission input shaft 17a and a loose gear 37a rotatably mounted on the second transmission output shaft 19a. The loose gears 35a, 37a mesh with the respective fixed gears 34a, 36a. The two shift units 32a, 33a connect the loose gears 35a, 37a to the respective transmission output shafts 18a, 19a in a rotationally fixed manner to select a particular transmission gear.

[0034] The transmission unit 15a includes a parking lock wheel 40a, which is designed for selectively locking the first transmission output shaft 18a. It is also conceivable in this context to arrange the parking lock wheel 40a in a different position that would appear advantageous to a person skilled in the art.

[0035] To transmit torque from the internal combustion engine 10a and / or the electric machine 11a to the transmission unit 15a, the hybrid drive device includes a planetary gear set 38a. The internal combustion engine 10a is connected to the planetary gear set 38a via a disconnect clutch 39a. The electric machine 11a is directly connected to the planetary gear set 38a. The two spur gear units 20a and 21a are directly connected to the planetary gear set 38a. Viewed in an axial direction 57a, the internal combustion engine 10a and the spur gear units 20a and 21a are arranged on opposite sides of the planetary gear set 38a.

[0036] The planetary gear set 38a comprises a first planet gear set 41a and a second planet gear set 42a. The first planet gear set 41a includes a first ring gear 43a, an outer planet gear set 44a, an inner planet gear set 45a, and a first sun gear 46a. The planet gear sets 44a and 45a each have a number of planet gears that would be considered reasonable by those skilled in the art, preferably three or four planet gears each. The planet gears are loose gears. The planetary gear set 38a includes a first carrier 47a, a second carrier 48a, and a third carrier 49a. More precisely, a carrier is a set of carriers consisting of a plurality of interconnected carriers arranged on a circular path, with each planet gear being mounted on its own carrier. The outer planet gear set 44a is mounted on the first carrier 47a. The inner planet gear set 45a is mounted on the second carrier 48a.The first carrier 47a is rotationally fixed to the second carrier 48a. The planet gears of the outer planetary gear set 44a mesh with the first ring gear 43a. The planet gears of the outer planetary gear set 44a mesh with the planet gears of the inner planetary gear set 45a. The planet gears of the inner planetary gear set 45a mesh with the first sun gear 46a. The outer planetary gear set 44a and the inner planetary gear set 45a thus form a double planetary gear set 44a, 45a with a first and second carrier 47a, 48a. The first sun gear 46a is connected to the disconnect clutch 39a via a drive shaft 58a. Thus, when the disconnect clutch 39a is closed, the first sun gear 46a is driven directly by the internal combustion engine 10a without any gear ratio.

[0037] The second planetary gear set 42a has a second ring gear 50a. The second planetary gear set 42a further has a planetary gear set 51a and a second sun gear 52a. The planetary gear set 51a has a number of planet gears that appears sensible to a person skilled in the art, preferably three or four planet gears. The planet gears form loose gears. The planetary gear set 38a includes the third web 49a. The third web 49a is non-rotatably connected to the second web 48a and the first web 47a. The planetary gear set 51a is mounted on the third web 49a. The planet gears of the planetary gear set 51a mesh with the second ring gear 50a. The planet gears of the planetary gear set 51a mesh with the second sun gear 52a. The second ring gear 50a is non-rotatably coupled to the rotor 13a of the electric machine 11a. The planetary gear 38a is designed as a five-shaft planetary gear 38a.

[0038] The first sun gear 46a, the double planetary gear set 44a, 45a, and the ring gear 43a are arranged in a first gear plane 53a of the planetary gear set 38a. The second sun gear 52a, the planetary gear set 51a, the second ring gear 50a, and the inner planetary gear set 45a are arranged in a second gear plane 54a of the planetary gear set 38a. The inner planetary gear set 45a is thus arranged within the first gear plane 53a and the second gear plane 54a.

[0039] The first, second and third webs 47a, 48a, 49a are each non-rotatably connected between the first and second gear planes 53a, 54a to the first partial gear input shaft 16a of the planetary gear 38a.

[0040] The planetary gear 38a includes a brake unit 55a. The brake unit 55a is designed to brake the first ring gear 43a. More precisely, the brake unit 55a is designed to brake the first ring gear 43a relative to the gear housing 14a.

[0041] Furthermore, the planetary gear set 38a includes a coupling unit 56a. The coupling unit 56a is designed for a rotationally fixed coupling of the second ring gear 50a with the second sun gear 52a. Thus, the coupling unit 56a is designed to lock the planetary gear set 38a. When the planetary gear set 38a is locked, the first and second partial gear set input shafts 16a, 17a rotate at the same speed as the first sun gear 46a. When the disengaging clutch 39a is closed, the first and second partial gear set input shafts 16a, 17a rotate at the same speed as the internal combustion engine 10a.

[0042] The first spur gear unit 20a and the second spur gear unit 21a, together with the planetary gear unit 38a, are configured to provide eleven different gear ratios. Specifically, the first spur gear unit 20a and the second spur gear unit 21a, together with the planetary gear unit 38a, are configured to provide two purely electrically driven gears. Furthermore, the first spur gear unit 20a and the second spur gear unit 21a, together with the planetary gear unit 38a, are configured to provide seven forward gears. Additionally, the first spur gear unit 20a and the second spur gear unit 21a, together with the planetary gear unit 38a, are configured to provide a non-load-shiftable overdrive. Finally, the first spur gear unit 20a and the second spur gear unit 21a, together with the planetary gear unit 38a, are configured to provide a mechanical reverse gear.

[0043] A switching strategy for switching the switching units 24a, 25a, 32a, 33a can be found in the table in Fig. 5. Seven forward gears G1, G2, G3, G4, G5, G6, G7, an overdrive OD (which engages seamlessly with the seventh forward gear G7), a normal reverse gear RW, and two purely electric forward gears E1, E2 are available. In the purely electric forward gears E1, E2, the transmission unit 15a is driven exclusively by the electric motor 11a. The forward gears G2, G4, G6 are intermediate gears that seamlessly bridge the shift points between the forward gears G1, G3, G5, G7 with the aid of the electric motor 11a. A mark in the corresponding row means that the corresponding switching unit 24a, 25a, 32a, 33a is closed, the disconnect clutch 39a is closed, the coupling unit 56a is closed and / or the brake unit 55a is braking in order to shift the gear shown in the first column.

[0044] In the Fig. Figure 6 shows a further embodiment of the invention. The following descriptions are essentially limited to the differences between the embodiments, whereby with regard to identical components, features and functions, reference is made to the description of the other embodiment, in particular the Fig. 1, Fig. 2, Fig. 3, Fig. 4 to Fig. 5, reference can be made. To distinguish the embodiments, the letter a in the reference numerals of the embodiment of the Fig. 1, Fig. 2, Fig. 3, Fig. 4 to Fig. 5 by the letter b in the reference numerals of the embodiment of the Fig. 6 replaced. With regard to identically designated components, in particular with regard to components with the same reference numerals, reference can generally also be made to the drawings and / or the description of the other embodiment, in particular the Fig. 1, Fig. 2, Fig. 3, Fig. 4 to Fig. 5, will be referred.

[0045] The hybrid drive system comprises an internal combustion engine 10b and an electric machine 11b. The electric machine 11b functions as an electric motor. Alternatively, a hydraulic or pneumatic drive unit with a corresponding energy storage device could be used instead of the electric machine 11b. The electric machine 11b is designed to convert either electrical energy into mechanical energy or vice versa. For this purpose, the electric machine 11b has a stator 12b and a rotor 13b. The stator 12b is rigidly connected to a gearbox housing 14b. The gearbox housing 14b is rotationally fixed and rigidly connected to the body of the hybrid vehicle. The rotor 13b is rotatably mounted relative to the stator 12b. The hybrid vehicle includes a battery (not shown) for the provision and storage of electrical energy.The battery device is designed to provide electrical energy for driving the electric machine 11b and to store electrical energy generated by the combustion engine 10b or supplied from an external power grid.

[0046] The hybrid drive device includes a transmission unit 15b for providing multiple gear ratios. To introduce drive torque, the transmission unit 15b has a first partial transmission input shaft 16b and a second partial transmission input shaft 17b. In contrast to the first embodiment, the first partial transmission input shaft 16b is designed as a hollow shaft. The second partial transmission input shaft 17b is also designed as a hollow shaft. The first partial transmission input shaft 16b and the second partial transmission input shaft 17b are arranged coaxially with each other. The second partial transmission input shaft 17b passes through the first partial transmission input shaft 16b.

[0047] To transmit a drive torque, i.e., an output torque, translated by the transmission unit 15b, the transmission unit 15b has a first transmission output shaft 18b and a second transmission output shaft 19b. The transmission output shafts 18b and 19b are arranged parallel to and offset from the partial transmission input shafts 16b and 17b. The transmission output shafts 18b and 19b are intended for connection to drive wheels of the hybrid vehicle (not shown in detail).

[0048] The gear unit 15b comprises a first spur gear unit 20b and a second spur gear unit 21b. The first spur gear unit 20b and the second spur gear unit 21b can be connected in parallel to each other in a power flow. The first spur gear unit 20b is arranged axially upstream of the second spur gear unit 21b.

[0049] The first spur gear unit 20b has two different gear ratios. The first spur gear unit 20b has the first sub-gearbox input shaft 16b. The drive torque is introduced into the first spur gear unit 20b via the first sub-gearbox input shaft 16b. To set the two different sub-gear ratios, the first spur gear unit 20b has a first gear pair 22b, a second gear pair 23b, a first shift unit 24b, and a second shift unit 25b. The first shift unit 24b is designed as a double shift unit. The first gear pair 22b has a fixed gear 26b mounted on the first sub-gearbox input shaft 16b and a loose gear 27b rotatably mounted on the first gearbox output shaft 18b. The second gear pair 23b has a fixed gear 28b fixedly arranged on the first partial transmission input shaft 16b and a loose gear 29b rotatably arranged on the second transmission output shaft 19b.The loose gears 27b, 29b mesh with the respective fixed gears 26b, 28b. The two switching units 24b, 25b connect the loose gears 27b, 29b to the respective transmission output shaft 18b, 19b in a rotationally fixed manner to select a respective transmission gear.

[0050] The second spur gear unit 21b has two different gear ratios. The second spur gear unit 21b has a second input shaft 17b. The drive torque is introduced into the second spur gear unit 21b via the second input shaft 17b. To adjust the two different gear ratios, the second spur gear unit 21b has a first gear pair 30b, a second gear pair 31b, a third shift unit 32b, and a fourth shift unit 33b. The third shift unit 32b is designed as a double shift unit together with the first shift unit 24b. The third gear pair 30b has a fixed gear 34b mounted on the second input shaft 17b and a loose gear 35b rotatably mounted on the first output shaft 18b.The fourth gear pair 31b comprises a fixed gear 36b mounted on the second partial transmission input shaft 17b and a loose gear 37b rotatably mounted on the second transmission output shaft 19b. The loose gears 35b and 37b mesh with the respective fixed gears 34b and 36b. The two shift units 32b and 33b connect the loose gears 35b and 37b to the respective transmission output shafts 18b and 19b in a rotationally fixed manner to select a particular transmission gear.

[0051] The transmission unit 15b includes a parking lock wheel 40b, which is provided for the selective locking of the first transmission output shaft 18b. In this context, it is also conceivable to arrange the parking lock wheel 40b in a different position that would appear sensible to a person skilled in the art.

[0052] To transmit torque from the internal combustion engine 10b and / or the electric machine 11b to the transmission unit 15b, the hybrid drive device includes a planetary gear 38b. The internal combustion engine 10b is connected to the planetary gear 38b via a disconnect clutch 39b.

[0053] The electric machine 11b is directly connected to the planetary gear set 38b. The two spur gear units 20b, 21b are also directly connected to the planetary gear set 38b. In contrast to the first embodiment, the internal combustion engine 10b and the spur gear units 20b, 21b are arranged on the same side of the planetary gear set 38b when viewed in an axial direction 57b. Thus, the internal combustion engine 10b and the planetary gear set 38b are arranged on opposite sides of the spur gear units 20b, 21b when viewed in an axial direction.

[0054] The planetary gear set 38b comprises a first planet gear set 41b and a second planet gear set 42b. The first planet gear set 41b includes a first ring gear 43b, an outer planet gear set 44b, an inner planet gear set 45b, and a first sun gear 46b. The planet gear sets 44b and 45b each have a number of planet gears that would be considered reasonable by a person skilled in the art, preferably three or four planet gears each. The planet gears are loose gears. The planetary gear set 38b includes a first carrier 47b, a second carrier 48b, and a third carrier 49b. More precisely, a carrier is a set of carriers consisting of a plurality of interconnected carriers arranged on a circular path, with each planet gear being mounted on its own carrier. The outer planet gear set 44b is mounted on the first carrier 47b. The inner planet gear set 45b is mounted on the second carrier 48b.The first carrier 47b is rotationally fixed to the second carrier 48b. The planet gears of the outer planetary gear set 44b mesh with the first ring gear 43b. The planet gears of the outer planetary gear set 44b mesh with the planet gears of the inner planetary gear set 45b. The planet gears of the inner planetary gear set 45b mesh with the first sun gear 46b. The outer planetary gear set 44b and the inner planetary gear set 45b thus form a double planetary gear set 44b, 45b with a first and second carrier 47b, 48b. The first sun gear 46b is connected to the disconnect clutch 39b via a drive shaft 58b. Thus, when the disconnect clutch 39a is closed, the first sun gear 46b is driven directly by the internal combustion engine 10b without any gear ratio. The drive shaft 58b is arranged coaxially with the partial transmission input shafts 16b, 17b. The drive shaft 58b passes through the partial transmission input shaft 17b.

[0055] The second planetary gear set 42b has a second ring gear 50b. The second planetary gear set 42b further comprises a planetary gear set 51b and a second sun gear 52b. The planetary gear set 51b has a number of planet gears that appears sensible to a person skilled in the art, preferably three or four planet gears. The planet gears form loose gears. The planetary gear set 38b includes the third web 49b. The third web 49b is non-rotatably connected to the second web 48b and the first web 47b. The planetary gear set 51b is mounted on the third web 49b. The planet gears of the planetary gear set 51b mesh with the second ring gear 50b. The planet gears of the planetary gear set 51b mesh with the second sun gear 52b. The second ring gear 50b is non-rotatably coupled to the rotor 13b of the electric machine 11b. The planetary gear 38b is designed as a five-shaft planetary gear 38b.

[0056] The first sun gear 46b, the double planetary gear set 44b, 45b, and the ring gear 43b are arranged in a first gear plane 53b of the planetary gear set 38b. The second sun gear 52b, the planetary gear set 51b, the second ring gear 50b, and the inner planetary gear set 45b are arranged in a second gear plane 54b of the planetary gear set 38b. The inner planetary gear set 45b is thus arranged within the first gear plane 53b and the second gear plane 54b.

[0057] The first, second and third web 47b, 48b, 49b are connected in a rotationally fixed manner between the first and second gear plane 53b, 54b to the second partial gear input shaft 17b of the planetary gear 38b.

[0058] The planetary gear 38b includes a brake unit 55b. The brake unit 55b is designed to brake the first ring gear 43b. More precisely, the brake unit 55b is designed to brake the first ring gear 43b relative to the gear housing 14b.

[0059] Furthermore, the planetary gear 38b includes a coupling unit 56b. In contrast to the first embodiment, the coupling unit 56b is designed for a rotationally fixed coupling of the first ring gear 43b with the first sun gear 46b. Thus, the coupling unit 56b is designed to lock the planetary gear 38b. When the planetary gear 38b is locked, the first and second partial gear input shafts 16b, 17b rotate at the same speed as the first sun gear 46b. When the disengaging clutch 39b is closed, the first and second partial gear input shafts 16b, 17b rotate at the same speed as the internal combustion engine 10b.

[0060] The first spur gear unit 20b and the second spur gear unit 21b, together with the planetary gear unit 38b, are designed to provide eleven different gear ratios. Specifically, the first spur gear unit 20b and the second spur gear unit 21b, together with the planetary gear unit 38b, are designed to provide two purely electrically driven gears. Furthermore, the first spur gear unit 20b and the second spur gear unit 21b, together with the planetary gear unit 38b, are designed to provide seven forward gears. Additionally, the first spur gear unit 20b and the second spur gear unit 21b, together with the planetary gear unit 38b, are designed to provide a non-load-shiftable overdrive. Finally, the first spur gear unit 20b and the second spur gear unit 21b, together with the planetary gear unit 38b, are designed to provide a mechanical reverse gear.

[0061] A switching strategy for switching the switching units 24b, 25b, 32b, 33b corresponds to the switching strategy of the first embodiment. Therefore, for the second embodiment, reference can be made to the switching table in Fig. 5 are referred to. Reference symbol list 10 Internal combustion engine 11 machine 12 Stator 13 Rotor 14 Gearbox housings 15 Gear unit 16 partial gearbox input shaft 17 partial gearbox input shaft 18 Gearbox output shaft 19 Transmission output shaft 20 spur gear units 21 Spur gear unit 22 gear pair 23 gear pair 24 switching unit 25 switching unit 26" fixed wheel 27 Loose wheel 28" fixed wheel 29 Loose wheel 30 gear pairs 31 gear pair 32 switching unit 33 Switching unit 34 Fixed wheel 35 Loose wheel 36 fixed wheel 37 Loose wheel 38 planetary gears 39 Disconnect coupling 40 parking lock wheel 41 Planetary gear set 42 Planetary gear set 43 Ring gear 44 Planetary Set 45 Planetary Set 46 Sun wheel 47 Bridge 48 Bridge 49 Bridge 50 ring gear 51 Planetary Set 52 Sun wheel 53 Gear plane 54 Gear plane 55 Brake unit 56 coupling unit 57 Axial direction 58 Drive shaft

Claims

[1] Hybrid drive device comprising an internal combustion engine (10a; 10b), an electric machine (11a; 11b), a planetary gear set (38a; 38b), a first spur gear set (20a; 20b) and a second spur gear set (21a; 21b), wherein the internal combustion engine (10a; 10b) is connected to the planetary gear set (38a; 38b) via a disconnecting clutch (39a; 39b) and the electric machine (11a; 11b) is directly connected to the planetary gear set (38a; 38b), wherein the two spur gear units (20a, 21a; 20b, 21b) are directly connected to the planetary gear set (38a; 38b), wherein the planetary gear set (38a; 38b) comprises a first planetary gear set (41a; 41b) and a second planetary gear set (42a, 42b), wherein the first planetary gear set (41a; 41b) comprises a first ring gear (43a; 43b) and a first sun gear (46a; 46b), wherein at least one web (47a, 48a) of a planetary gear set (44a; 44b; 45a; 45b) of the first planetary gear set (41a; 41b) and at least one web (49a, 49b) of a planetary gear set (51a, 51b) of the second planetary gear set (42a; 42b) are connected to each other in a rotationally fixed manner, wherein the second planetary gear set (42a; 42b) has a second ring gear (50a; 50b), and wherein the second ring gear (50a; 50b) is coupled non-rotatably to a rotor (13a; 13b) of the electric machine (11a; 11b), characterized by , that the first planetary gear set (41a; 41b) comprises an outer planetary gear set (44a; 44b) and an inner planetary gear set (45a; 45b), wherein the outer planetary gear set (44a; 44b) and the inner planetary gear set (45a; 45b) form a double planetary gear set with a first and second rib (47a, 48a; 47b, 48b), and that the second planetary gear set (42a; 42b) comprises the planetary gear set (51a; 51b) of the second planetary gear set (42a; 42b) with a third rib (49a; 49b), wherein the first, second and third ribs (47a, 48a, 49a; 47b, 48b, 49b) are rotationally fixed to one another. [2] Hybrid drive device according to claim 1, characterized by , that the second planetary gear set (42a; 42b) has a second sun gear (52a; 52b). [3] Hybrid drive device according to any of the preceding claims, characterized by, that the planetary gear (38a; 38b) has a brake unit (55a; 55b) which is intended for the immediate braking of a shaft of the planetary gear (38a; 38b). [4] Hybrid drive device according to any of the preceding claims, characterized by , that the planetary gear (38a; 38b) has a coupling unit (56a; 56b) which is provided for a rotationally fixed coupling of two shafts of the planetary gear (38a; 38b). [5] Hybrid drive device according to any of the preceding claims, characterized by , that the first sun gear (46a; 46b), the double planetary gear set and the first ring gear (43a; 43b) are arranged in a first gear plane (53a; 53b) of the planetary gear set (38a; 38b). [6] Hybrid drive device according to claim 5, characterized by, that the second sun gear (52a; 52b), the planetary set (51a; 51b) of the second planetary gear set (42a; 42b), the second ring gear (50a; 50b) and the inner planetary set (45a; 45b) are arranged in a second gear plane (54a; 54b) of the planetary gear set (38a; 38b). [7] Hybrid drive device according to any of the preceding claims, characterized by , that the first, second and third web (47a, 48a, 49a; 47b, 48b, 49b) between a first and second gear plane (53a, 54a; 53b, 54b) are connected in a rotationally fixed manner to a partial gear input shaft (16a; 17b) of the planetary gear (38a; 38b). [8] Hybrid drive device according to claim 3, characterized by , that the brake unit (55a; 55b) is designed to brake the first ring gear (43a; 43b). [9] Hybrid drive device according to claim 4, characterized by , that the coupling unit (56a) is provided for a rotationally fixed coupling of the second ring gear (50a) with the second sun gear (52a). [10] Hybrid drive device according to any of the preceding claims, characterized by , that the second sun gear (52a) is connected in a rotationally fixed manner to a second partial gear input shaft (17a) of the planetary gear (38a). [11] Hybrid drive device according to claim 10, characterized by , that the second partial transmission input shaft (17a; 17b) is designed as a hollow shaft. [12] Hybrid drive device according to claim 6, characterized by , that the inner planetary set (45a; 45b) is arranged within the first gear plane (53a; 53b) and the second gear plane (54a; 54b). [13] Hybrid drive device according to any of the preceding claims, characterized by , that the first spur gear unit (20a; 20b) and the second spur gear unit (21a; 21b) together with the planetary gear unit (38a; 38b) are provided for a transmission of at least eleven different gears. [14] Hybrid drive device according to any one of claims 1 to 13, characterized by , that the internal combustion engine (10a) and the spur gear units (20a, 21a) are arranged on different sides of the planetary gear unit (38a) when viewed in an axial direction (57a). [15] Hybrid drive device according to any one of claims 1 to 13, characterized by , that the internal combustion engine (10b) and the planetary gear (38b) are arranged on different sides of the spur gear unit (20b, 21b) when viewed in an axial direction (57b).

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