DE102019207884B4 - Transmission arrangement for a hybrid vehicle and hybrid vehicle - Google Patents

Abstract

Gear arrangement (10) for a hybrid vehicle, with:- a housing (12),- a Ravigneaux set (28) which has exactly one ring gear (30) which is rotatable relative to the housing (12), a first sun gear (34), a second sun gear (36), a first planetary gear set (38), a second planetary gear set (40) and a planet carrier (42) on which the planetary gear sets (38, 40) are rotatably mounted,- an output shaft (44) which is connected in a rotationally fixed manner to the ring gear (30) and is rotatable relative to the housing (12), via which torques can be discharged from the Ravigneaux set (28),- a drive shaft (46) which is connected in a rotationally fixed manner to the second sun gear (36) and is rotatable relative to the housing (12), via which torques can be introduced into the Ravigneaux set (28),- a connection element (48) with which an output shaft (16) of a Internal combustion engine (14),- a first clutch (K1), by means of which the connecting element (48) can be coupled to the planet carrier (42),- a second clutch (K2), by means of which the connecting element (48) can be coupled to the drive shaft (46),- a first brake (B1), by means of which the first sun gear (34) can be secured to the housing (12),- a second brake (B2), by means of which the planet carrier (42) can be secured to the housing (12), and- an electric machine (18) arranged concentrically to the drive shaft (46), by means of which the drive shaft (46) can be driven; characterized in that the Ravigneaux set (28) is at least partially covered outwards in the radial direction (54) of the Ravigneaux set (28) by at least one of the clutches (K1, K2) and/or by at least one of the brakes (B1, B2), wherein the at least one clutch (K1, K2) and/or the at least one brake (B1, B2) is arranged within the electrical machine (18).

Description

The invention relates to a transmission arrangement for a hybrid vehicle and a hybrid vehicle with such a transmission arrangement.

WO 2016/0 75 334 A1 discloses a torque transmission device for a motor vehicle, with an input shaft and with a first planetary gear set, which has as first gear elements at least a first planetary gear for meshing with a first sun gear and with a first ring gear of the first planetary gear set and a planetary carrier for rotatably supporting at least one of the first planetary gears. In addition, the EN 10 2014 223 339 A1 a torque transmission device as known.

Furthermore, an automatic transmission is known from US 2016 / 0 272 059 A1. The EN 11 2006 002 068 B4 An electrically adjustable transmission is known to be taken. The FR 2 838 679 A1 also discloses a transmission for a vehicle. In addition, the EN 10 2016 226 090 A1 a torque transmission device is known.

The object of the present invention is to provide a transmission arrangement and a hybrid vehicle so that a particularly advantageous drive of the hybrid vehicle can be realized in a particularly space-saving manner.

This object is achieved according to the invention by a transmission arrangement with the features of patent claim 1 and by a hybrid vehicle with the features of patent claim 12. Advantageous embodiments with expedient further developments of the invention are specified in the remaining claims.

A first aspect of the invention relates to a transmission arrangement for a hybrid vehicle, which is preferably designed as a motor vehicle, in particular as a passenger car. The transmission arrangement has a housing and a Ravigneaux set, which is also referred to as a Ravigneaux planetary set or Ravigneaux planetary gear set. The Ravigneaux set is arranged, for example, at least partially, in particular at least predominantly or completely, in the housing of the transmission arrangement. The Ravigneaux set has exactly one ring gear that can rotate relative to the housing, a first sun gear, a second sun gear, a first planetary gear set and a second planetary gear set. In addition, the Ravigneaux set has, in particular exactly, one planet carrier. The first planetary gear set and the second planetary gear set are rotatably mounted on the planet carrier common to the planetary gear sets. The first planetary gear set has, for example, at least one or more first planet gears, wherein the at least one first planet gear is rotatably mounted on the planet carrier. the second planetary gear set has, for example, at least one or more second planetary gears, wherein the at least one second planetary gear is rotatably mounted on the planet carrier. It is preferably provided that the Ravigneaux set has a single ring gear in the form of the aforementioned ring gear, wherein the single ring gear of the Ravigneaux set is rotatable relative to the housing, in particular about an axis of rotation.

Furthermore, it is preferably provided that the Ravigneaux set has exactly two sun gears, one of the exactly two sun gears being the first sun gear and the other of the exactly two sun gears being the second sun gear. Furthermore, it is preferably provided that the Ravigneaux set has exactly one planet carrier in the form of the aforementioned planet carrier. The sun gears and the planet carrier are, for example, particularly when they are not fixed to the housing, i.e. are not connected to the housing in a rotationally fixed manner or are coupled to the housing, rotatable relative to the housing, in particular about the aforementioned axis of rotation. The sun gears are preferably of different sizes. This means that the sun gears can have different diameters, in particular external diameters, from one another. For example, the second sun gear is larger than the first sun gear, so that the second sun gear can have a larger diameter, in particular a larger external diameter, than the first sun gear. Alternatively, it is conceivable that the sun gears are the same size, i.e. have the same diameter. The first planetary gear set meshes, for example, with the ring gear and with the first sun gear at the same time, in particular while the first planetary gear set does not mesh with the second sun gear. In other words, it is preferably provided that the first planetary gear set does not mesh with the second sun gear.

The second planetary gear set meshes, for example, with the second sun gear and at the same time with the first planetary gear set, in particular while the second planetary gear set meshes with the ring gear. In other words, it is preferably provided that the second planetary gear set does not mesh with the ring gear. For example, the first planetary gear set has a first extension running in the axial direction of the Ravigneaux set, in particular a first length, wherein the second planetary gear set has a first extension running in the axial direction of the Ravigneaux set. fenden second extension, in particular second length. The axial direction of the Ravigneaux set coincides with the previously mentioned axis of rotation. Preferably, the second extension, in particular the second length, is greater than the first extension, in particular the first length. In particular, it is conceivable that the first planetary gear set, in particular its first planetary gears, meshes with the second planetary gear set, in particular its second planetary gears.

The gear arrangement further comprises an output shaft which is connected to the ring gear in a particularly permanent and rotationally fixed manner and which can rotate relative to the housing, in particular about the axis of rotation, via which torques can be diverted from the Ravigneaux set, i.e. can be discharged from the Ravigneaux set. The torques which can be diverted from the Ravigneaux set via the output shaft are also referred to below as first torques. In the context of the present invention, for example, the feature that two components are permanently connected to one another in a rotationally fixed manner is to be understood as meaning that these components are permanently and therefore always connected to one another in a rotationally fixed manner, so that no switching element is provided by means of which the rotationally fixed connection of the components could be selectively, reversibly and alternately canceled and established. Since the first torques can be derived from the Ravigneaux set via the output shaft, and since the output shaft is connected, in particular permanently, to the ring gear in a rotationally fixed manner, the ring gear and the output shaft form an output via which the first torques can be derived from the Ravigneaux set. The first torques can be used to drive, for example, vehicle wheels of the hybrid vehicle, also referred to as wheels, and thus the hybrid vehicle as a whole. The vehicle wheels are, for example, ground contact elements via which the hybrid vehicle is or can be supported on a ground in the vertical direction of the vehicle. If the hybrid vehicle is driven along the ground while the hybrid vehicle is supported on the ground via the vehicle wheels in the vertical direction of the vehicle, the vehicle wheels roll on the ground.

The gear arrangement also includes a drive shaft that is connected, in particular permanently, in a rotationally fixed manner to the second sun gear and can rotate relative to the housing, in particular about the axis of rotation, and via which torques can be introduced into the Ravigneaux set. The torques that can be introduced into the Ravigneaux set via the drive shaft are also referred to below as second torques. The second sun gear and thus the Ravigneaux set can thus be driven by means of the second torques and thus via the drive shaft. For this purpose, the second torques are transmitted to the second sun gear via the drive shaft and thereby introduced into the Ravigneaux set. The first torques result, for example, from the second torques and can be provided by the Ravigneaux set via the ring gear and output from the Ravigneaux set via the output shaft, i.e. can be removed from the ring gear.

The gear arrangement further comprises a connection element, designed for example as a connection shaft and also referred to as a connection or connection part, to which an output shaft of an internal combustion engine can be coupled, in particular in a torque-transmitting manner. This means that the connection element can be driven by the output shaft and thus by the internal combustion engine. The internal combustion engine, designed for example as a reciprocating piston engine, can provide third torques for driving the hybrid vehicle, in particular for driving the aforementioned vehicle wheels, via its output shaft, designed for example as a crankshaft. The internal combustion engine can provide the third torques via the output shaft. The third torques can be transmitted from the output shaft to the connection element, so that the connection element can be driven by means of the third torques and can thereby be rotated, for example, about the axis of rotation relative to the housing.

The gear arrangement has a first clutch, by means of which the connecting element can be coupled to the planet carrier, in particular connected in a rotationally fixed manner. Thus, for example, the third torques transmitted to the connecting element can be transmitted to the planet carrier via the first clutch. This allows the planet carrier to be driven and thus rotated relative to the housing, for example, in particular about the axis of rotation. In particular, the third torques can be transmitted to the planet carrier via the connecting element and thus introduced into the Ravigneaux set via the planet carrier.

Since the second torques can be introduced into the Ravigneaux set via the drive shaft, whereby the Ravigneaux set can be driven, and since the drive shaft is connected, in particular permanently, to the second sun gear in a rotationally fixed manner, the second sun gear and the drive shaft form, for example, a first input. The second torques can be introduced into the Ravigneaux set via the first input. , whereby the Ravigneaux set can be driven. Since the third torques can be introduced into the Ravigneaux set via the connecting element and the planet carrier, whereby the Ravigneaux set can be driven by means of the third torques, the connecting element and the planet carrier, for example, form a second input of the Ravigneaux set. The third torques can be introduced into the Ravigneaux set via the second input, whereby the Ravigneaux set can be driven. For example, the first torques can result from the third torques introduced into the Ravigneaux set. In particular, it is conceivable that the first torques result from the second torques introduced into the Ravigneaux set and from the third torques introduced into the Ravigneaux set.

The gear arrangement also includes a second clutch, by means of which the connecting element can be coupled to the drive shaft, in particular connected in a rotationally fixed manner. Thus, for example, the third torques transmitted to the connecting element can be transmitted via the second clutch to the drive shaft and thus to the second sun gear, so that, for example, the third torques can be introduced into the Ravigneaux set via the second sun gear. This can drive the Ravigneaux set. The respective clutch is designed, for example, as a frictional or force-locking clutch. In particular, the respective clutch can be designed as a separating clutch and/or as a friction clutch, in particular as a multi-disk clutch. It is thus conceivable that, for example, the connecting element can be frictionally coupled to the planet carrier by means of the first clutch. Alternatively or additionally, the connecting element can be frictionally connected to the drive shaft by means of the second clutch. It is also conceivable that the respective clutch is designed as a positive clutch. The positive clutch can be a claw clutch, for example. It is therefore conceivable, for example, that the connecting element can be positively coupled to the planet carrier using the first clutch. Alternatively or additionally, the connecting element can be positively coupled to the drive shaft using the second clutch, for example.

The gear arrangement further comprises a first brake, by means of which the first sun gear can be secured to the housing, i.e. can be connected to the housing in a rotationally fixed manner. The gear arrangement further comprises a second brake, by means of which the planet carrier can be secured to the housing, i.e. can be connected to the housing in a rotationally fixed manner. It is preferably provided that the gear arrangement has exactly two clutches in the form of the aforementioned clutches. In other words, it is preferably provided that the gear arrangement has the two clutches as the only clutches. Alternatively or additionally, it can be provided that the gear arrangement has exactly two brakes in the form of the aforementioned brakes, so that it is preferably provided that the gear arrangement has the aforementioned brakes as the only brakes.

The clutch and the brakes are switching elements whose functions are explained in more detail below: The first clutch can, for example, be switched or adjusted between at least one first coupling state and at least one first decoupling state. In the first coupling state, the connecting element is coupled to the planet carrier via the first clutch or by means of the first clutch, so that torques between the connecting element and the planet carrier can be transmitted via the first clutch. In particular, in the first coupling state, the connecting element is connected to the planet carrier in a rotationally fixed manner by means of the first clutch, so that, for example, when the connecting element is driven, the connecting element and the planet carrier rotate together and thus relative to the housing, in particular about the axis of rotation. In the first decoupling state, however, the connecting element is decoupled from the planet carrier, so that the connecting element can rotate relative to the planet carrier, in particular about the axis of rotation. In particular, the first clutch can be moved relative to the housing and/or translationally between at least one first coupling position and at least one first decoupling position. The first coupling state is set by moving the first clutch into the first coupling position. By moving the first clutch to the first decoupling position, the first decoupling state is set.

The previous statements on the first clutch can be transferred mutatis mutandis, i.e. with corresponding changes, to the second clutch with regard to the connecting element and the drive shaft. Thus, for example, the second clutch can be adjusted or switched between at least one second coupling state and at least one second decoupling state. In the second coupling state, the connecting element is coupled to the drive shaft via the second clutch or by means of the second clutch, in particular in a torque-transmitting manner, so that Torques can be transmitted between the connection element and the drive shaft via the second clutch. In particular, in the second coupling state, the connection element is connected to the drive shaft in a rotationally fixed manner by means of the second clutch, so that, for example, when the connection element is driven, the connection element and the drive shaft rotate together and thus rotate together, in particular about the axis of rotation, relative to the housing. In the second decoupling state, however, the connection element is decoupled from the drive shaft, so that the connection element can rotate relative to the drive shaft, in particular about the axis of rotation. The second clutch can, for example, be moved relative to the housing and/or translationally between at least one second coupling position and at least one second decoupling position. The second coupling state is set by moving the second clutch into the second coupling position. The second decoupling state is set, for example, by moving the second clutch into the second decoupling position.

The first brake can be adjusted or switched, for example, between at least one third coupling state and at least one third decoupling state. In the third coupling state, the first sun gear is fixed to the housing via the first brake or by means of the first brake, so that the first sun gear does not or cannot rotate relative to the housing even when torques are transmitted to the first sun gear. In the third decoupling state, however, the first sun gear is rotatable relative to the housing, in particular about the axis of rotation, so that the first sun gear rotates or can rotate relative to the housing, in particular about the axis of rotation, when the first sun gear is driven, that is, when torques are transmitted to the first sun gear. The first brake can be moved, for example, between at least one third coupling position and at least one third decoupling position relative to the housing and/or translationally. By moving the first brake to the third coupling position, for example, the third coupling state is set. By moving the first brake to the third decoupling position, for example, the third decoupling state is set.

The previous statements on the first brake can be applied mutatis mutandis, i.e. with corresponding changes, to the second brake with regard to the planet carrier and the housing. The second brake can thus be adjusted or switched between at least one fourth coupling state and at least one fourth decoupling state, for example. In the fourth coupling state, the planet carrier is fixed to the housing via the second brake or by means of the second brake, i.e. is connected to the housing in a rotationally fixed manner. The planet carrier cannot rotate relative to the housing or the planet carrier does not rotate relative to the housing even when torques are transmitted to the planet carrier. In the fourth decoupling state, however, the planet carrier is decoupled from the housing or can rotate relative to the housing, in particular about the axis of rotation, so that the planet carrier rotates or can rotate relative to the housing, in particular about the axis of rotation, when the planet carrier is driven, i.e. when torques are transmitted to the planet carrier. For example, the second brake can be moved relative to the housing and/or translationally between at least one fourth coupling position and at least one fourth decoupling position. By moving the second brake to the fourth coupling position, the fourth coupling state is set. By moving the second brake to the fourth decoupling position, for example, the fourth decoupling state is set.

The respective brake is, for example, a frictional or force-locking brake. The brake can be designed as a multi-disk brake, for example. It is also conceivable that the respective brake is a positive-locking brake and, for example, a claw clutch. It is therefore conceivable that the second sun gear or the planet carrier can be secured to the housing by means of the respective brake in a frictional or force-locking or positive-locking manner.

In order to be able to realize a particularly advantageous operation or drive of the hybrid vehicle in a particularly space-saving manner, the transmission arrangement also includes an electric machine arranged concentrically to the drive shaft, by means of which the drive shaft can be driven. Thus, for example, the electric machine can provide the second torques and exert them on the drive shaft and, via the drive shaft, on the second sun gear. Thus, for example, the aforementioned vehicle wheels and the hybrid vehicle as a whole can be driven by means of the electric machine, in particular electrically and preferably purely electrically.

The electric machine has, for example, a stator and a rotor, which can be driven by the stator and thereby rotated by a Machine rotation axis is rotatable relative to the stator.

In order to be able to keep the installation space requirement of the gear arrangement particularly low, in particular in the axial direction, it is provided according to the invention that the Ravigneaux set is at least partially covered outwards in the radial direction of the Ravigneaux set by at least one of the clutches and/or by at least one of the brakes, wherein this at least one clutch and/or this at least one brake is arranged inside the electric machine. In other words, the at least one clutch, in particular both clutches, and/or the at least one brake, in particular both brakes, are arranged around the Ravigneaux set, in particular in the circumferential direction of the Ravigneaux set. The at least one clutch and/or the at least one brake is at least partially covered outwards in the radial direction by the stator and/or by the rotor of the electric machine. This makes it possible to create a particularly short length of the gear arrangement running in the axial direction of the gear arrangement.

The feature that the electric machine is arranged concentrically to the drive shaft can be understood in particular to mean that the rotor is arranged concentrically to the drive shaft. Since the drive shaft is rotatable about the axis of rotation relative to the housing, and since the rotor is rotatable about the machine axis of rotation relative to the stator and relative to the housing, and since the rotor is arranged concentrically to the drive shaft, the machine axis of rotation coincides with the axis of rotation, for example.

In the fully manufactured state of the hybrid vehicle, it comprises the transmission arrangement according to the invention. It is preferably provided that in the fully manufactured state the axis of rotation and thus the machine axis of rotation runs in the transverse direction of the vehicle, so that the transmission arrangement is arranged or installed transversely.

Because the transmission arrangement has the electric machine, the clutches and the brakes, several switchable gears, in particular at least or exactly four switchable gears, of the transmission arrangement can be implemented in a particularly space-saving manner. This means that the transmission arrangement according to the invention can be designed as a multi-speed, hybridized transmission, by means of which a particularly efficient and effective drive of the hybrid vehicle can be implemented in a particularly space-saving manner. In particular, the invention makes it possible to keep the axial installation space requirement of the transmission arrangement particularly low. In other words, in the axial direction of the Ravigneaux set and in the axial direction of the transmission arrangement as a whole, a short form or design of the transmission arrangement, which is also referred to as the transmission structure, can be represented.

It has proven to be particularly advantageous if the Ravigneaux set is arranged at least partially, in particular at least predominantly or completely, in the electric machine, i.e. inside the electric machine, in the axial direction of the gear arrangement, i.e. along the axial direction of the gear arrangement and thus viewed in the axial direction of the Ravigneaux set. This is to be understood in particular that the Ravigneaux set is covered at least partially, in particular at least predominantly or completely, by the rotor and/or the stator of the electric machine in the radial direction of the Ravigneaux set and thus in the radial direction of the electric machine of the gear arrangement as a whole. This means that the axial installation space requirement of the gear arrangement can be kept to a particularly small extent.

In a particularly advantageous embodiment of the invention, the rotor of the electric machine, which is arranged concentrically to the drive shaft, is connected to the drive shaft in a rotationally fixed manner, in particular permanently. This means that the number of parts, the weight, the costs and the installation space required can be kept to a particularly low level.

A further embodiment is characterized in that the second clutch has a first clutch element, which is in particular permanently connected to the connecting element in a rotationally fixed manner, and a second clutch element, which is in particular permanently connected to the drive shaft in a rotationally fixed manner. In relation to a torque flow running from the connecting element via the first clutch to the planet carrier, the first clutch element is connected to the connecting element upstream of the first clutch, in particular permanently connected to the connecting element in a rotationally fixed manner. For example, the aforementioned third torques provided by the internal combustion engine via the output shaft can be transmitted from the connecting element via the first clutch to the planet carrier via the aforementioned torque flow or along the torque flow. Since the first clutch is preferably connected to the connecting element upstream of the first clutch and not downstream of the first clutch, in particular permanently connected to the connecting element in a rotationally fixed manner, for example, the connecting element can be connected to the planet carrier via the first clutch. element and thus the output shaft of the internal combustion engine are coupled, in particular connected in a rotationally fixed manner, to the drive shaft and thus, for example, to the second sun gear and/or to the electric machine, in particular to the rotor, by means of the second clutch, while the first clutch is open, i.e. while the connecting element is decoupled from the planet carrier. As a result, for example, the output shaft can drive the drive shaft and thus the rotor and/or the second sun gear via the second clutch, while the planet carrier is not driven via the first clutch and by the output shaft. As a result, a particularly advantageous operation of the hybrid vehicle can be achieved in a particularly space-saving manner.

A further embodiment provides that one of the clutches, in particular the first clutch, is arranged on a first side of the Ravigneaux set. In other words, one clutch, in particular the first clutch, is arranged in the axial direction of the Ravigneaux set, i.e., viewed along the axial direction, on this side of the Ravigneaux set. The other clutch, in particular the second clutch, is preferably arranged on a second side of the Ravigneaux set facing away from the first side in the axial direction. Thus, for example, the other clutch, in particular the second clutch, is arranged in the axial direction of the Ravigneaux set, i.e., viewed along the axial direction, on the other side of the Ravigneaux set. This makes it possible to achieve a particularly compact design of the transmission arrangement.

It has proven to be particularly advantageous if the brakes are arranged between the clutches in the axial direction of the Ravigneaux set. This does not necessarily mean that the brakes are covered in the axial direction by one clutch, i.e. by the other clutch.

In a particularly advantageous embodiment of the invention, the couplings are arranged on the same side of the Ravigneaux set and thus on the other side or this side of the Ravigneaux set. This also makes it possible to achieve a particularly compact structure.

In order to be able to realize a particularly advantageous operation, in particular a particularly advantageous drive, of the hybrid vehicle in a particularly space-saving manner, the transmission arrangement in a further embodiment of the invention comprises an axle transmission which can be driven by the ring gear. In its fully manufactured state, the hybrid vehicle has, for example, at least or exactly two axles which are arranged one behind the other or one after the other in the longitudinal direction of the vehicle. One of the axles has the transmission arrangement according to the invention. The axle having the transmission arrangement is preferably a rear axle or a front axle of the hybrid vehicle. The axle comprises the vehicle wheels mentioned above. In particular, the axle has at least or exactly two vehicle wheels in the form of the vehicle wheels mentioned above, the vehicle wheels being spaced apart from one another in the transverse direction of the vehicle. The vehicle wheels of the axle can be driven by the internal combustion engine and the electric machine via the axle transmission. In particular, the vehicle wheels can be driven via the axle gear using the first torques, so that, for example, the respective first torque, which can be provided or is provided by the Ravigneaux set via its ring gear, is transmitted to the vehicle wheels by means of the axle gear, in particular divided or distributed between the vehicle wheels. The axle gear thus has its function, which is already well known from the general state of the art, of transmitting the respective first torque to the vehicle wheels, in particular distributing or splitting it between the vehicle wheels, and, for example, allowing different speeds of the vehicle wheels when the hybrid vehicle is cornering. Thus, for example, when cornering, the vehicle wheel on the outside of the curve rotates at a higher speed than the vehicle wheel on the inside of the curve. In particular, the axle gear can be designed as a differential gear, which is also simply referred to as a differential or axle differential. In particular, the differential gear can be designed as a bevel gear differential or as a spur gear differential.

The gear arrangement further comprises at least one spur gear stage, via which the axle gear can be driven by the Ravigneaux set, in particular by the ring gear. The at least one spur gear stage has a first gear, which is in particular permanently and rotationally fixedly connected to the ring gear, and a second gear which can be driven by the first gear and via which the axle gear can be driven by the first gear. Thus, it is provided, for example, that with respect to a torque flow running from the ring gear via the spur gear stage to the axle gear, the first gear is arranged downstream of the ring gear, the second gear is arranged downstream of the first gear and the axle gear is arranged downstream of the second gear. For example, the second gear meshes with the first gear.
It has proven to be particularly advantageous if the spur gear stage is arranged in the axial direction of the Ravigneaux set between the Ravigneaux set and at least one of the clutches, in particular between the Ravigneaux set and both clutches. This ensures a particularly compact design of the gear arrangement, in particular in the axial direction.

In order to keep the axial installation space requirement particularly low, it is provided in a further embodiment of the invention that at least one of the clutches, in particular both clutches, are arranged on a first side of the spur gear stage, wherein the electric machine is arranged on a second side of the spur gear stage facing away from the first side of the spur gear stage in the axial direction.

In a further embodiment of the invention, the electrical machine is designed as a transverse flux machine, which is also referred to as an axial flux machine. This allows the installation space requirement and the weight to be kept particularly low.

Finally, it has proven to be particularly advantageous if the brakes are arranged one after the other in the radial direction of the Ravigneaux set and thus in the radial direction of the gear arrangement as a whole. This means that one of the brakes is arranged at least partially, in particular at least predominantly or completely, further out than the other brake in the radial direction towards the outside. It is particularly conceivable that the other brake is covered at least partially, in particular at least predominantly or completely, by the one brake in the radial direction towards the outside. This means that the axial installation space requirement can be kept to a particularly small extent.

A second aspect of the invention relates to a hybrid vehicle, preferably designed as a motor vehicle, in particular as a passenger car. The hybrid vehicle comprises an internal combustion engine with an output shaft, wherein the hybrid vehicle can be driven by means of the internal combustion engine via the output shaft. The hybrid vehicle also comprises a transmission arrangement, in particular according to the first aspect of the invention. The transmission arrangement has a housing and a Ravigneaux set. The Ravigneaux set has exactly one ring gear that can rotate relative to the housing, a first sun gear, a second sun gear, a first planetary gear set, a second planetary gear set and a planet carrier. The planetary gear sets are rotatably mounted on the planet carrier. The transmission arrangement also has an output shaft that is, in particular permanently, connected to the ring gear in a rotationally fixed manner and is rotatable relative to the housing, via which torques can be output from the Ravigneaux set. The gear arrangement also includes a drive shaft, which is connected to the second sun gear in a rotationally fixed manner, in particular permanently, and is rotatable relative to the housing, via which torques can be introduced into the Ravigneaux set. In addition, a connecting element that can be driven by the output shaft is provided, wherein, for example, the output shaft can be coupled or is coupled to the connecting element, in particular in a torque-transmitting manner. In particular, it is conceivable that the output shaft is permanently coupled to the connecting element in a torque-transmitting manner, in particular permanently connected in a rotationally fixed manner.

The gear arrangement further comprises a first clutch, by means of which the connecting element can be coupled to the planet carrier, in particular connected in a rotationally fixed manner. In addition, the gear arrangement also comprises a second clutch, by means of which the connecting element can be coupled to the drive shaft, in particular connected in a rotationally fixed manner. The gear arrangement further comprises a first brake, by means of which the first sun gear can be fixed to the housing, i.e. connected in a rotationally fixed manner to the housing. In addition, a second brake is provided, by means of which the planet carrier can be fixed to the housing, i.e. connected in a rotationally fixed manner to the housing. Furthermore, the gear arrangement comprises an electric machine arranged concentrically to the drive shaft, by means of which the drive shaft can be driven. Advantages and advantageous embodiments of the first aspect of the invention are to be regarded as advantages and advantageous embodiments of the second aspect of the invention and vice versa.

According to the invention, the Ravigneaux set is at least partially covered outwards in the radial direction of the Ravigneaux set by at least one of the clutches and/or by at least one of the brakes, wherein the at least one clutch and/or the at least one brake is arranged within the electrical machine.

The invention also includes further developments of the hybrid vehicle according to the invention, which have features as have already been described in connection with the further developments of the transmission arrangement according to the invention. For this reason, the corresponding further developments of the hybrid vehicle according to the invention are not described again here.

The hybrid vehicle according to the invention is a motor vehicle and is preferably designed as a motor vehicle, in particular as a passenger car or a truck, or as a passenger bus or a motorcycle. The invention also includes combinations of the features of the described embodiments.

• 1 eine schematische Strukturdarstellung einer erfindungsgemäße Getriebeanordnung;
• 2 eine schematische Anordnungsdarstellung einer ersten Ausführungsform der Getriebeanordnung;
• 3 eine schematische Anordnungsdarstellung der Getriebeanordnung gemäß der zweiten Ausführungsform;
• 4 eine Schaltmatrix zur Veranschaulichung von Getriebemodi der Getriebeanordnung, insbesondere gemäß der ersten und zweiten Ausführungsform;
• 5 eine schematische Anordnungsdarstellung der Getriebeanordnung gemäß einer dritten Ausführungsform;
• 6 eine schematische Darstellung der Getriebeanordnung gemäß einer vierten Ausführungsform.

Exemplary embodiments of the invention are described below.

• 1 a schematic structural representation of a gear arrangement according to the invention;
• 2 a schematic arrangement representation of a first embodiment of the transmission arrangement;
• 3 a schematic arrangement diagram of the transmission arrangement according to the second embodiment;
• 4 a switching matrix for illustrating transmission modes of the transmission arrangement, in particular according to the first and second embodiments;
• 5 a schematic arrangement representation of the transmission arrangement according to a third embodiment;
• 6 a schematic representation of the transmission arrangement according to a fourth embodiment.

The exemplary embodiments explained below are preferred embodiments of the invention. In the exemplary embodiments, the components of the embodiments described each represent individual features of the invention that are to be considered independently of one another and which also develop the invention independently of one another. Therefore, the disclosure should also include combinations of the features of the embodiments other than those shown. Furthermore, the described embodiments can also be supplemented by other features of the invention already described.

In the figures, identical reference symbols designate functionally identical elements.

1 shows a schematic structural representation of a transmission arrangement 10 for a motor vehicle designed as a hybrid vehicle. The representation in 1 merely shows links between the individual components, i.e. for example their interfaces, and does not necessarily give an indication of their structural arrangement. The gear arrangement 10 comprises a 1 particularly schematically illustrated housing 12, which is also referred to, for example, as a transmission housing. In a fully manufactured state, the motor vehicle comprises the transmission arrangement 10 and an internal combustion engine 14, designed, for example, as a reciprocating piston machine, by means of which the motor vehicle can be driven by an internal combustion engine. The internal combustion engine 14 has an output shaft 16, designed, for example, as a crankshaft, via which the internal combustion engine 14 can provide drive torques for driving the hybrid vehicle. In particular, in its fully manufactured state, the hybrid vehicle has at least or exactly two axles arranged one behind the other in the longitudinal direction of the vehicle and thus consecutive, one of the axles being a front axle and the other axle being a rear axle. The transmission arrangement 10 is assigned, for example, to the rear axle or the front axle. In other words, the rear axle or the front axle comprises, for example, the transmission arrangement 10. The respective axle has at least or exactly two vehicle wheels spaced apart from one another in the transverse direction of the vehicle and also simply referred to as wheels, via which the hybrid vehicle is or can be supported downwards on a ground in the vertical direction of the vehicle. The vehicle wheels of the axle that has the transmission arrangement 10 can be driven by the internal combustion engine 14 via its output shaft 16 and thus by means of the drive torques. As will be explained in more detail below, the transmission arrangement 10 comprises at least or exactly one electric machine 18, so that the axle that includes the transmission arrangement 10 comprises the electric machine 18. The vehicle wheels of the axle that includes the transmission arrangement 10 can be driven electrically by the electric machine 18. The motor vehicle can thus be driven by an internal combustion engine and electrically. The axle that includes the transmission arrangement 10 preferably comprises the electric machine 18 as the only electric machine.

The output shaft 16 is rotatable about a motor rotation axis 20 relative to the housing 12. The internal combustion engine 14 can be installed transversely or built in transversely, so that, for example, the motor rotation axis 20 runs in the transverse direction of the vehicle. It is also conceivable that the internal combustion engine 14 is installed longitudinally or built in longitudinally. So that, for example, the motor rotation axis 20 runs in the longitudinal direction of the vehicle. The electric machine 18 has a stator 22 and a rotor 24. The rotor 24 can be driven by the stator 22 and can therefore be rotated about a machine rotation axis 26 relative to the stator 22. The electric machine 18 is installed transversely or built in transversely. installed so that the machine rotation axis 26 runs in the transverse direction of the vehicle.

The gear arrangement 10 has, in particular at least or exactly, one Ravigneaux set 28, which can be arranged at least partially, in particular at least predominantly or completely, in the housing 12. The Ravigneaux set 28 has exactly one ring gear 30, which is rotatable about an axis of rotation 32 relative to the housing 12. In addition, the Ravigneaux set 28 comprises a first sun gear 34, a second sun gear 36, a first planetary gear set 38, a second planetary gear set 40 and a planet carrier 42 common to the planetary gear sets 38 and 40, on which the planetary gear sets 38 and 40 are rotatably mounted, in particular simultaneously. 1 it can be seen that the first planetary gear set 38 meshes simultaneously with the sun gear 34 and with the ring gear 30, whereby the planetary gear set 38 does not mesh with the sun gear 36. The planetary gear set 40 meshes simultaneously with the sun gear 36 and with the planetary gear set 38, whereby the planetary gear set 40 does not mesh with the ring gear 30. In other words, first planet gears of the planetary gear set 38 mesh with second planet gears of the planetary gear set 40. The planetary gear set 38 has a first length running in the axial direction of the Ravigneaux set 28, whereby the second planetary gear set 40 has a second length running in the axial direction of the Ravigneaux set 28. The second length is greater than the first length, so that the planetary gear set 40 can simultaneously mesh with the sun gear 36 and with the planetary gear set 38, which is arranged in the axial direction following the sun gear 36. The axial direction of the Ravigneaux set 28 coincides with the axis of rotation 32, wherein the axial direction of the Ravigneaux set 28 corresponds to the axial direction of the electric machine 18 and the gear arrangement 10 as a whole.

The gear arrangement 10 has an output shaft 44 which is connected in a rotationally fixed manner to the ring gear 30 and via which first torques can be output from the Ravigneaux set 28, i.e. can be discharged from the Ravigneaux set 28. The Ravigneaux set 28 can thus provide the first torques via the ring gear 30. The first torques can be transmitted from the ring gear 30 to the output shaft 44 and finally to the vehicle wheels in order to drive the vehicle wheels. The gear arrangement 10 also has a drive shaft 46 which is connected in a rotationally fixed manner to the second sun gear 36 and which can rotate about the axis of rotation 32 relative to the housing 12. Second torques, in particular those provided by the electric machine 18 via the rotor 24, can be introduced into the Ravigneaux set 28 via the drive shaft 46. In addition, as will be explained in more detail below, third torques can be introduced into the Ravigneaux set 28 via the drive shaft 46. The third torques are, for example, the drive torques mentioned above. In other words, the third torques can be provided by the internal combustion engine 14 via the output shaft 16.

The gear arrangement 10 also has a connecting element 48, designed for example as a shaft, in particular as a connecting shaft, to which the output shaft 16 can be coupled, in particular connected in a rotationally fixed manner. This means that the connecting element 48 is driven by the output shaft 16 and can therefore be rotated, for example, about the axis of rotation 32 relative to the housing 12. In other words, the drive torques or the third torques can be transmitted from the output shaft 16 to the connecting element 48. In addition, the third torques can be transmitted, for example, to the drive shaft 46 and thus, for example, to the rotor 24.

The hybrid vehicle has a flywheel 50, in this case designed as a dual-mass flywheel, via which, for example, the connecting element 48 can be driven by the output shaft 16 and thus by the internal combustion engine 14. In particular, the connecting element 48 is permanently coupled to the output shaft 16 via the flywheel 50, in particular permanently connected in a rotationally fixed manner to the output shaft 16. The transmission arrangement 10 also has a first clutch K1, by means of which the connecting element 48 can be coupled to the planet carrier 42, in particular connected in a rotationally fixed manner. The third torques provided by the internal combustion engine 14 via the output shaft 16 and transmitted from the output shaft 16 via the flywheel 50 to the connecting element 48 can thus be transmitted to the planet carrier 42 via the first clutch K1 and thus introduced into the Ravigneaux set 28 via the planet carrier 42.

Furthermore, the gear arrangement 10 comprises a second clutch K2, by means of which the connecting element 48 can be coupled to the AW 46, in particular connected in a rotationally fixed manner. Thus, for example, the third torques can be transmitted from the connecting element 48 via the second clutch K2 to the drive shaft 46 and thus, for example, to the rotor 24 and/or to the sun gear 36. As a result, for example, the third torques can be transmitted via the sun gear 36 into the Ravigneaux set 28. The gear arrangement 10 also has a first brake B1, by means of which the first sun gear can be secured to the housing 12. Furthermore, the gear arrangement 10 comprises a second brake B2, by means of which the planet carrier 42 can be secured to the housing 12.

In order to be able to realize a particularly advantageous operation or drive of the hybrid vehicle in a particularly space-efficient manner, the transmission arrangement 10 comprises the electric machine 18, which is arranged concentrically to the drive shaft 46. In addition, the drive shaft 46 can be driven by means of the electric machine 18. In particular, the rotor 24 is arranged concentrically to the drive shaft 46, so that the machine rotation axis 26 coincides with the rotation axis 32. Furthermore, it can preferably be provided that the rotor 24 is connected, in particular permanently, to the drive shaft 46 in a rotationally fixed manner. The second torques provided by the electric machine 18 via the rotor 24 can thus be transmitted from the rotor 24 to the drive shaft 46 and from the drive shaft 46 to the sun gear 36 and introduced into the Ravigneaux set 28 via the drive shaft 46 and via the sun gear 36. Furthermore, it is conceivable that the third torques are transmitted via the connecting element 48 and the second clutch K2 to the drive shaft 46 and with the drive shaft 46 to the rotor 24.

2 shows a first embodiment of the gear arrangement 10. 2 it can be seen that the Ravigneaux set 28 is arranged at least partially, in particular at least predominantly or completely, within the electric machine 18 in the axial direction, that is to say viewed along the axial direction of the gear arrangement 10. Thus, in the radial direction of the gear arrangement 10, the Ravigneaux set 28 is at least partially, in particular at least predominantly or completely, covered by the electric machine 18, that is to say by the stator 22 and/or by the rotor 24, towards the outside. In addition, in the present second embodiment, the brakes B1 and B2 are arranged in the circumferential direction of the Ravigneaux set 28 around its circumference, so that the Ravigneaux set 28 is at least partially covered by the respective brakes B1 and B2 towards the outside in the radial direction. Furthermore, the clutch K2 is arranged at least partially, in particular at least predominantly or completely, within the electric machine 18 when viewed along the axial direction and is thus covered in the radial direction towards the outside at least partially, in particular at least predominantly or completely, by the electric machine 18 and thus by the rotor 24 and/or the stator 22. In 2 the axial direction of the Ravigneaux set 28 and thus of the electric machine 18 and the gear arrangement 10 as a whole is illustrated by a double arrow 52. In addition, 2 the radial direction of the Ravigneaux set 28, and thus of the electric machine 18 and of the gear arrangement 10 as a whole, which is perpendicular to the axial direction, is illustrated by a double arrow 54. The two brakes B1 and B2 are also arranged at least partially, in particular at least predominantly or completely, within the electric machine 18 when viewed along the axial direction, so that in the second embodiment both brakes B1 and B2 are covered in the radial direction towards the outside at least partially, in particular at least predominantly or completely, by the electric machine 18, that is to say by the stator 22 and/or the rotor 24.

Particularly good looking 1 it can be seen that the second clutch K2 has a first clutch element 56 which is connected in a rotationally fixed manner to the connection element 48 and a second clutch element 58 which is connected in a rotationally fixed manner to the drive shaft 46. If the clutch K2 is in its closed state and thus in its coupling state, for example the clutch elements 56 and 58 and thus the connection element 48 and the drive shaft 46 are coupled to one another in a torque-transmitting manner, in particular are connected in a rotationally fixed manner, so that torques can be transmitted between the clutch elements 56 and 58 or between the connection element 48 and the drive shaft 46. However, if the clutch K2 is in its open state and thus in its uncoupled state, the clutch elements 56 and 58 and thus the drive shaft 46 and the connection element 48 are decoupled from one another, so that, for example, no torques can be transmitted between the clutch elements 56 and 58 or between the drive shaft 46 and the connection element 48. In particular, the coupling elements 56 and 58 or the drive shaft 46 and the connection element 48 can then rotate relative to one another about the rotation axis 32. In relation to a torque flow running from the connection element 48 via the first clutch K1 to the planet carrier 42, via or along which, for example, the third torques can be transmitted from the connection element 48 via the clutch K1 to the planet carrier 42, the coupling element 56 is connected in a rotationally fixed manner to the connection element 48 upstream of the first clutch K1, i.e. at a point S arranged upstream of the first clutch K1.

At the 2 In the first embodiment shown, the second clutch K2 is arranged on a first side S1 of the Ravigneaux set 28, while the first clutch K1 is arranged on a second side S2 of the Ravigneaux set 28 facing away from the first side S1 in the axial direction. Both brakes B1 and B2 are arranged in the axial direction between the clutches K1 and K2.

In the second embodiment, the gear arrangement 10 comprises an axle gear 60, designed for example as a differential gear, in particular as a bevel gear differential. This means that the axle has the axle gear 60. The vehicle wheels can be driven by the output shaft 44 via the axle gear 60. Fourth torques, for example, result from the first torques, which are provided by the Ravigneaux set 28 via the ring gear 30 and transmitted to the output shaft 44. The respective fourth torque is, for example, introduced into the axle gear 60, whereby the axle gear 60 is driven. The respective fourth torque or a respective fifth torque resulting from the respective fourth torque is transmitted to the vehicle wheels, for example by means of the axle gear 60, and in particular divided or distributed between the vehicle wheels, so that ultimately, for example, the vehicle wheels are driven by means of the respective fifth torque.

The gear arrangement 10 comprises a gear device 62 with a first spur gear stage 64 and a second spur gear stage 66. The first spur gear stage 64 comprises a first gear 68 which is connected, in particular permanently, in a rotationally fixed manner to the ring gear 30 and a second gear 70 which meshes with the gear 68 and can be driven by the gear 68. The axle gear 60 can be driven by the gear 70 so that the axle gear 60 can be driven by the gear 68 via the gear 70. The second spur gear stage 66 comprises the gear 70 and a third gear 72 which meshes with the gear 70. The gear 70 is rotatable, for example, about an axis of rotation 74 relative to the housing 12, the axis of rotation 74 being, for example, spaced from the axis of rotation 32 and running parallel to the axis of rotation 32. The axle gear 60 can be driven, for example, by the gear 72, so that the axle gear 60 can be driven by the gear 70 via the gear 72. For example, the gear 72 is permanently connected in a rotationally fixed manner to the axle gear 60, in particular to a differential head of the axle gear 60. The spur gear stages 64 and 66 are arranged in the axial direction between the Ravigneaux set 28 and the first clutch K1. The clutch K2 is arranged on a first side S3 of the respective spur gear stage 64 or 66, while the clutch K1 is arranged on a second side S4 of the respective spur gear stage 64 or 66, which faces away from the first side S3 in the axial direction. In the second embodiment, it is conceivable that the brakes B1 and B2 are arranged at the same height in the radial direction.
In the first embodiment, for example, an intermediate shaft can be provided which is rotatable about the rotation axis 74 relative to the housing 12. As an alternative to the 2 In the embodiment shown, it is possible that the gear 70 is connected, in particular permanently, in a rotationally fixed manner to the intermediate shaft, and that, for example, the gear 72 does not mesh with the gear 70, but is arranged following the gear 70 in the axial direction of the intermediate shaft and is, in particular permanently, in a rotationally fixed manner to the intermediate shaft. Then, for example, the axle gear 60 can be driven by the gear 72 and via the gear 72 by the intermediate shaft, so that, for example, the gear 72 can be driven via the intermediate shaft by the gear 72.

3 shows a schematic representation of a second embodiment of the gear arrangement 10. In the second embodiment, both clutches K1 and K2 are arranged on the same side S2 of the Ravigneaux set 28, and preferably also on the same side S4 of the respective spur gear stage 64 or 66.

4 shows a switching matrix, based on which different transmission modes, also referred to as operating modes, of the transmission arrangement 10, in particular according to the first and second embodiments, are explained below. The clutches K1 and K2 and the brakes B1 and B2 are also referred to collectively as switching elements. In the 4 shown switching matrix, a respective closed state or a respective coupling state of the respective switching element is designated with an “x”, whereby the respective switching element to which no “x” is assigned is open and is thus in a decoupling state. From 4 it can be seen that a first of the transmission modes is a first internal combustion engine operation V1, a second of the transmission modes is a second internal combustion engine operation V2, a third of the transmission modes is a third internal combustion engine operation V3 and a fourth of the transmission modes is a fourth internal combustion engine operation V4. It is conceivable that in the respective internal combustion engine operation V1, V2, V3 and V4 the vehicle wheels and thus the hybrid vehicle with respect to the internal combustion engine 14 and the electric machine 18 are driven exclusively by means of the internal combustion engine. machine 14 can be driven or are driven. Alternatively, it is conceivable that in the respective combustion engine operation V1, V2, V3 and V4 the vehicle wheels and thus the hybrid vehicle can be driven or are driven both by the combustion engine 14 and by the electric machine 18. The respective combustion engine operation V1, V2, V3 and V4 can therefore also be referred to as a combustion engine gear or hybrid gear, for example.

First of all, it should be explained that it can be provided that the electric machine 18 can be operated optionally in a motor mode and in a generator mode. In the motor mode, the electric machine 18 is operated as an electric motor, which in the motor mode can provide the respective second torque for electrical driving via the rotor 24. Thus, in the motor mode, the rotor 24 is driven by the stator 22, so that in the motor mode the vehicle wheels can be or are driven by the electric machine 18. In the generator mode, the electric machine 18 is operated as a generator. In the generator mode, the rotor 24 is driven by the rotating vehicle wheels and thus by kinetic energy of the moving hybrid vehicle and/or by the output shaft 16, so that mechanical energy, by means of which the rotor 24 is driven, is converted into electrical energy by means of the generator. This electrical energy can be provided by the generator and stored, for example, in a battery. If, for example, the electric machine 18 is operated in engine mode in the respective internal combustion engine mode V1, V2, V3 and V4, the hybrid vehicle is driven both by the internal combustion engine 14 and by the electric machine 18 and is therefore hybrid-driven. However, if, for example, the electric machine 18 is operated as a generator in the respective internal combustion engine mode V1, V2, V3 and V4, the hybrid vehicle is driven exclusively by the internal combustion engine 14 with respect to the internal combustion engine 14 and the electric machine 18.

In the internal combustion engine mode V1, the clutch K2 and the brake B1 are closed at the same time, while the clutch K1 and the brake B2 are opened at the same time. In the internal combustion engine mode V2, the clutch K2 and the brake B2 are closed at the same time, while the clutch K1 and the brake B1 are opened at the same time. In the internal combustion engine mode V3, the clutches K1 and K2 are closed at the same time, while the brakes B1 and B2 are opened at the same time. In the internal combustion engine mode V4, the clutch K1 and the brake B2 are closed at the same time, while the clutch K2 and the brake B1 are opened at the same time.

A fifth of the transmission modes is an electric motor operation E1, and a sixth of the transmission modes is an electric motor operation E2. In the respective electric motor operation E1 or E2, for example, the vehicle wheels and thus the hybrid vehicle with respect to the internal combustion engine 14 and the electric machine 18 are driven exclusively by means of the electric machine 18, wherein it is preferably provided that the output shaft 16 is not driven by the electric machine 18. For this purpose, in the respective electric motor operation E1 or E2, the clutches K1 and K2 are opened simultaneously. In the first electric motor operation E1, the clutches K1 and K2 and the brake B2 are opened simultaneously, while the brake B1 is closed. In the electric motor operation E2, the clutches K1 and K2 and the brake B1 are opened simultaneously, while the brake B2 is closed.

A seventh of the transmission modes is a so-called CVT operation (CVT - continuously variable transmission). The CVT operation is designated CVT. In the CVT operation CVT, the clutch K2 and the brakes B1 and B2 are opened simultaneously, while the clutch K1 is closed. As a result, for example, in particular by driving the sun gear 36 by means of the electric machine 18, a ratio of the Ravigneaux set 28, in particular from the sun gear 36 to the ring gear 30, can be set or changed at least substantially continuously.

An eighth of the transmission modes is a stand-by charging mode SL, which is also referred to as stand-by charging. In the stand-by charging mode SL, the clutch K1 and the brakes B1 and B2 are opened simultaneously, while the clutch K2 is closed. This allows, for example, the internal combustion engine 14 to drive the rotor 24 via the output shaft 16 and the Ravigneaux set 28, in particular while the hybrid vehicle is not driven by the internal combustion engine 14. In this way, for example, the aforementioned battery can be charged while the hybrid vehicle is at a standstill.

5 shows a schematic representation of a third embodiment of the transmission arrangement 10. In the third embodiment, the electric machine 18 is designed as a transverse flux machine. The brakes B1 and B2 are arranged in the axial direction between the respective spur gear stage 64 or 66 and the electric machine 18, with the brakes B1 and B2 being arranged on the same side S3 of the respective spur gear stage 64 or 66. In addition, the brakes B1 and B2 are arranged one after the other in the radial direction, with the brake B1 being arranged further outwards in the radial direction than the brake B2. In particular, the brakes B1 and B2 can be positioned relative to one another along the axial direction in such a way that the brake B2 is at least partially, in particular at least predominantly or completely, covered by the brake B1 in the radial direction outwards.

Finally, 6 in a schematic representation of a fourth embodiment of the gear arrangement 10. While in the third embodiment the respective spur gear stage 64 or 66 is arranged in the axial direction between the clutches K1 and K2, in the fourth embodiment both clutches K1 and K2 are arranged on the same side S4 of the respective spur gear stage 64 or 66. 4 and in particular the 4 The operating modes shown also apply to the third and fourth embodiments.

Claims (12)

Gear arrangement (10) for a hybrid vehicle, with: - a housing (12), - a Ravigneaux set (28) which has exactly one ring gear (30) which is rotatable relative to the housing (12), a first sun gear (34), a second sun gear (36), a first planetary gear set (38), a second planetary gear set (40) and a planet carrier (42) on which the planetary gear sets (38, 40) are rotatably mounted, - an output shaft (44) which is connected in a rotationally fixed manner to the ring gear (30) and is rotatable relative to the housing (12), via which torques can be discharged from the Ravigneaux set (28), - a drive shaft (46) which is connected in a rotationally fixed manner to the second sun gear (36) and is rotatable relative to the housing (12), via which torques can be introduced into the Ravigneaux set (28), - a connection element (48) with which an output shaft (16) of a Internal combustion engine (14), - a first clutch (K1), by means of which the connecting element (48) can be coupled to the planet carrier (42), - a second clutch (K2), by means of which the connecting element (48) can be coupled to the drive shaft (46), - a first brake (B1), by means of which the first sun gear (34) can be secured to the housing (12), - a second brake (B2), by means of which the planet carrier (42) can be secured to the housing (12), and - an electric machine (18) arranged concentrically to the drive shaft (46), by means of which the drive shaft (46) can be driven; characterized in that the Ravigneaux set (28) is at least partially covered outwards in the radial direction (54) of the Ravigneaux set (28) by at least one of the clutches (K1, K2) and/or by at least one of the brakes (B1, B2), wherein the at least one clutch (K1, K2) and/or the at least one brake (B1, B2) is arranged within the electrical machine (18). Gear arrangement (10) according to Claim 1 , characterized in that the electric machine (18) has a rotor (24) arranged concentrically to the drive shaft (46) and connected in a rotationally fixed manner to the drive shaft (46). Gear arrangement (10) according to one of the preceding claims, characterized in that the second clutch (K2) has a first clutch element (56) connected in a rotationally fixed manner to the connecting element (48) and a second clutch element (58) connected in a rotationally fixed manner to the drive shaft (46), wherein the first clutch element (56) upstream of the first clutch (K1) is connected in a rotationally fixed manner to the connecting element (48) with respect to a torque flow running from the connecting element (48) via the first clutch (K1) to the planet carrier (42). Gear arrangement (10) according to one of the preceding claims, characterized in that one of the clutches (K1, K2), in particular the second clutch (K2), is arranged on a first side (S1) of the Ravigneaux set (28) and the other clutch (K1, K2), in particular the first clutch (K1), is arranged on a second side (S2) of the Ravigneaux set (28) facing away from the first side (S1) in the axial direction (52) of the Ravigneaux set (28). Gear arrangement (10) according to Claim 4 , characterized in that the brakes (B1) are arranged in the axial direction of the Ravigneaux set (28) between the clutches (K1, K2). Gear arrangement (10) according to one of the Claims 1 until 3 , characterized in that the couplings (K1, K2) are arranged in the axial direction (52) on the same side (S2) of the Ravigneaux set (28). Gear arrangement (10) according to one of the preceding claims, characterized by : - an axle gear (60) which can be driven by the ring gear (30), and - at least one spur gear stage (64, 66) which has a first gear (68) connected in a rotationally fixed manner to the ring gear (30) and a second gear (70) which can be driven by the first gear (68), via which the axle gear (60) can be driven by the first gear (68). Gear arrangement (10) according to Claim 7 , characterized in that the spur gear stage (64, 66) is arranged in the axial direction (52) of the Ravigneaux set (28) between the Ravigneaux set (28) and at least one of the clutches (K1, K2), in particular between the Ravigneaux set (28) and both clutches (K1, K2). Gear arrangement (10) according to Claim 8 , characterized in that the at least one of the clutches (K1, K2), in particular both clutches (K1, K2), are arranged on a first side (S4) of the spur gear stage (64, 66), wherein the electric machine (18) is arranged on a second side (S3) of the spur gear stage (64, 66) facing away from the first side (S4) of the spur gear stage (64, 66) in the axial direction (52). Gear arrangement (10) according to one of the preceding claims, characterized in that the electrical machine (18) is designed as a transverse flux machine. Gear arrangement (10) according to one of the preceding claims, characterized in that the brakes (B1, B2) are arranged one after the other in the radial direction (54). Hybrid vehicle, with an internal combustion engine (14) having an output shaft (16), by means of which the hybrid vehicle can be driven via the output shaft (16), and with a transmission arrangement (10) which has: - a housing (12), - a Ravigneaux set (28) which has exactly one ring gear (30) which can be rotated relative to the housing (12), a first sun gear (34), a second sun gear (36), a first planetary gear set (38), a second planetary gear set (40) and a planet carrier (42) on which the planetary gear sets (38, 40) are rotatably mounted, - an output shaft (44) which is connected in a rotationally fixed manner to the ring gear (30) and is rotatable relative to the housing (12), via which torques can be derived from the Ravigneaux set (28), - a drive shaft (46) which is connected in a rotationally fixed manner to the second sun gear (36) and is rotatable relative to the housing (12), via which torques can be introduced into the Ravigneaux set (28), - a connecting element (48) which can be driven by the output shaft (16), - a first clutch (K1), by means of which the connecting element (48) can be coupled to the planet carrier (42), - a second clutch (K2), by means of which the connecting element (48) can be coupled to the drive shaft (46), - a first brake (B1), by means of which the first sun gear (34) can be fixed to the housing (12), - a second brake (B2), by means of which the planet carrier (42) can be fixed to the housing (12), and - an electrical machine (18) arranged concentrically to the drive shaft (46), by means of which the drive shaft (46) can be driven; characterized in that the Ravigneaux set (28) is at least partially covered outwards in the radial direction (54) of the Ravigneaux set (28) by at least one of the clutches (K1, K2) and/or by at least one of the brakes (B1, B2), wherein the at least one clutch (K1, K2) and/or the at least one brake (B1, B2) is arranged within the electrical machine (18).

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