DE102021111476B3 - Drive device with a drive machine, a gear, a clutch and a locking device - Google Patents

Abstract

The invention relates to a planetary drive (11) which is provided with at least one stepped planetary gear set (12), a first planetary carrier (13), a sun gear (14) and a ring gear (15) and a clutch (6), the ring gear (15) meshes with planet gears (18, 19) of the stepped planetary gear set (12). A repeatedly switchable first active connection (W1) is formed between the ring gear (15) and the housing (16) via the clutch (6). The clutch surrounds at least one section of the ring gear on the outer circumference.

Description

field of invention

The invention relates to a drive device according to the preamble of claim 1.

Background of the Invention

Such a driving device is out DE 10 2013 225 519 A1 known. The drive device of an electric vehicle has an electric motor as the drive machine, a two-speed gearbox designed as a planetary drive, and a bevel gear differential. A double-acting clutch is provided in the drive device. The prime mover, gearbox, differential and clutch are housed in a common two-part housing and arranged coaxially with one another. The planetary drive consists of a sun gear, a set of stepped planetary gears and two ring gears. The planet carrier of the planetary drive and the differential carrier of the differential are constructed together and are connected to one another in one piece. The rotor shaft of the electric motor is connected to the input shaft of the planetary drive. A sun gear of the planetary drive sits on the input shaft.

The planetary drive consists of the sun gear, a stepped planetary gear set, the planetary carrier and two ring gears. The stepped planetary gear set is formed from individual stepped planetary gears which are carried by the first planet carrier. Each of the step planets has a large planetary gear with a large diameter and small planetary gear with a small diameter. The respective large planetary gear is coaxially connected in a torsionally rigid manner to the respective small planetary gear so as to transmit torque.

The set of large planetary gears meshes with a ring gear and the sun gear. The set of small planetary gears meshes with the other ring gear. A repeatedly switchable clutch is arranged between the respective ring gear and the housing of the drive device.

A repeatedly switchable operative connection is formed between the ring gears and the housing by selectively opening or closing the clutches. The clutches are designed in such a way that they can be engaged individually, independently of one another, but also synchronously with one another. The respective ring gear is fixed to the housing when the clutch is engaged, so that one or the other translation can be switched. In addition, a locking operative connection can be established by engaging or braking both clutches. When both clutches are engaged, both ring gears are fixed to the housing and the planetary drive is locked against power transmission. This switching state is selected in the sense of a parking or locking brake unit when the electric motor is switched off when the electric vehicle is stationary.

the DE 11 2011 104 355 T5 shows a multi-speed transmission, comprising: a sun gear; a high speed planetary gear in constant mesh with the sun gear and a high speed ring gear, the high speed planetary gear rotating about the sun gear; a low speed planetary gear connected to the high speed planetary gear and in constant mesh with a low speed ring gear; a carrier rotatably engaged with the high speed planetary gear and the low speed planetary gear such that either the high speed planetary gear or the low speed planetary gear controls the rotation of the carrier; a gear case surrounding the high-speed ring gear and the low-speed ring gear; and a clutch disposed adjacent to the high speed ring gear and the low speed ring gear, the clutch selectively connecting the high speed ring gear or the low speed ring gear to the transmission housing.

the WO 2018/ 099 542 A1 shows a shiftable two-speed transmission for the transmission of propulsion power within a motor vehicle drive train, comprising a rotationally driven input member via which the propulsion power is introduced into the transmission when propulsion power is being transmitted, and an output member via which the propulsion power is derived from the transmission, with the input member and Depending on the switching position of a switchable clutch, a direct drive or a transmission stage with a transmission ratio that differs from the direct drive can be implemented as an output element, and the three subassemblies external wheel unit, planetary unit and sun unit are provided, with the propulsive power transmission being introduced into the transmission via the external wheel unit.

the U.S. 5,807,205 A shows a parking lock of a drive device of an electric vehicle.

the WO 2017/ 129 173 A1 shows a planetary gear for a motor vehicle, comprising at least one drive shaft, at least one output shaft and at least one between the at least one drive shaft and the at least a stepped planetary gearset arranged on an output shaft and drivingly connected thereto, the stepped planetary gearset meshing with a first and a second ring gear, the first ring gear also being fixed in a stationary manner on a housing of the planetary gear, and the second ring gear being able to be fixed in a stationary manner on the housing via a switching element to block the at least one stepped planetary gearset, wherein the at least one output shaft is connected to a web, wherein the at least one stepped planetary gearset is rotatably mounted on the web.

the DE 103 38 659 A1 shows an electric drive unit for a motor vehicle, comprising: a stub axle; an electric motor with a stator fixed with respect to the stub axle and a rotor mounted rotatably with respect to the stub axle; a transmission having an input connected to the rotor for torque transmission; a wheel carrier connected to the output of the transmission for torque transmission; and that a first bearing of the wheel carrier is provided on a first axial side of the electric motor that faces away from the transmission; and that a second bearing of the wheel carrier - is either also provided on the first axial side of the electric motor, - or is provided in the gear, realized by a bearing of a rotatable gear part (directly or indirectly) connected to the wheel carrier.

the DE 10 2018 208 583 A1 shows a power-shiftable multi-speed transmission with at least one stepped planetary gear, which rotates around a first sun gear and rotates in a first ring gear, with the first ring gear rotating in a lockable freewheel and a first planetary gear stage of the at least one stepped planetary gear running in a first ring gear, while a second planetary gear stage in rotates a second ring gear, which is associated with at least one brake.

Description of the invention

The object of the invention is to further develop a drive device. The object is achieved by a device according to claim 1. Further developments of the device are the subject matter of the dependent claims.

The planetary drive is provided with at least one stepped planetary gear set and a first planetary carrier, at least one sun gear and at least one ring gear and at least one clutch. The stepped planet set is formed from individual, preferably three or four, stepped planets. Each of the stepped planetary gears has a first planetary gear and a second planetary gear coaxially connected to it in a torsionally rigid manner. The planets are optionally connected to one another in a form-fitting and/or non-positive and/or cohesive manner or are formed together in one piece in one piece. The ring gear meshes with a set of planet wheels of the stepped planetary set. A repeatedly switchable first operative connection is formed between the ring gear and the housing via the clutch. The clutch surrounds at least one section of the ring gear on the outer circumference.

The clutch is preferably arranged on the outer circumference of the ring gear. This allows space to be saved. Alternatively, the clutch can also be positioned at any other suitable location in the drive device.

The advantage of the invention lies in a very short axial design of the planetary drive.

The repeatedly switchable active connection between the ring gear and the housing can be produced, for example, by a brake, but preferably by a clutch. Via the brake, for example a band brake, or via the clutch, for example a multi-plate clutch, the torques acting on the ring gear can be partially or fully supported in the half-closed frictional connection or in the closed state.

The terms “operative connection” or “operatively connected” mean a connection between at least two devices, assemblies or components or combinations of these elements mentioned in the application with one another. The effect of the respective operative connection is only aligned in one direction or in both directions between the connected elements and is, for example, a torque-transmitting or torque-supporting connection between at least two elements.

According to the invention it is provided that at least one roller bearing is arranged concentrically to a common axis of rotation of the ring gear, the sun gear and the roller bearing. The second planet gears are distributed around the roller bearing at a radial distance from the roller bearing and are in toothed engagement with the ring gear.

The advantage of the invention lies in a very short axial design of the planetary drive. This has a particularly positive effect on use in modern electric motor-driven drive units in which the distance between the driven wheels or between the axles is limited.

One embodiment of the invention provides that at least one planetary carrier is mounted so as to be rotatable about the axis of rotation by means of the roller bearing, as a result of which additional axial space is saved compared to conventional planetary drives.

An embodiment of the invention provides that at least the sun gear is mounted with the roller bearing, whereby tilting in the system of the planetary drive can be supported in the event of uneven loading.

The last-mentioned positive effect can be further improved with an embodiment of the invention in which the toothing plane of the internal gear runs through the clutch. The toothing plane is an imaginary radial plane pierced perpendicularly by the axis of rotation of the ring gear, which runs in the middle of the effective width of a toothing of at least two of the second planet gears and that of the ring gear.

An embodiment of the invention provides that the toothing of the sun wheel is arranged axially next to the roller bearing, whereby the radial dimensions of the roller bearing are reduced, ie can be at least partially adapted to the radial level of the toothing of the sun wheel. As a result, radial installation space can be optimally utilized.

In order to avoid additional tilting, as an embodiment of the invention provides, the toothing plane runs radially through the roller bearing.

An embodiment of the invention provides that instead of only one carrier cheek of a planetary carrier, two carrier cheeks of either one and the same planetary carrier or of two separate planetary carriers are supported on the roller bearing. The carrier cheeks are attached to each other. Such a radial and axial nesting of the components in one another and with one another can take up a great deal of structural space in the radial and, in particular, in the axial direction.

• - Ein Ausgang ist als eine Funktionseinheit gesehen, über welche gewöhnlich Leistung aus einer Antriebsmaschine, einem Getriebe, wie einem Planetengetriebe, Differenzial oder aus einem Abschnitt der vorgenannten Getriebe an eine weitere Funktionseinheit weitergegeben wird.
• - Ein Eingang ist als eine Funktionseinheit gesehen, über welche gewöhnlich Leistung in eine Antriebsmaschine, ein Getriebe, wie ein Planetengetriebe, Differenzial oder in einen Abschnitt der vorgenannten Getriebe eingebracht wird.
• - Es ist nicht ausgeschlossen, dass auch Leistung in umgekehrter Richtung über den Ausgang eingebracht wird und Leistung über den Eingang an eine weitere Funktionseinheit weitergegeben wird. Die geschieht zum Beispiel bei Rekuperation, beim Bremsen oder Feststellen oder im Schubbetrieb.
• - Funktionseinheiten sind einzelne Maschinenelemente wie Wellen, Zahnräder, Planetenträger, Gehäuse, Kupplungen oder deren einzelne Elemente, Gehäuse und weitere geeignete Maschinenelemente, die geeignet sind, Leistungen aufzunehmen oder abzugeben bzw. Drehmomente zu übertragen bzw. abzustützen.

In general:

• - An output is seen as a functional unit via which power from a prime mover, a transmission such as a planetary gear, differential or from a section of the aforementioned transmission is usually passed on to another functional unit.
• - An input is seen as a functional unit through which power is usually introduced into a prime mover, a transmission such as a planetary gear, differential or into a portion of the aforementioned transmissions.
• - It cannot be ruled out that power is also introduced in the opposite direction via the output and power is passed on to another functional unit via the input. This happens, for example, during recuperation, when braking or locking or when coasting.
• - Functional units are individual machine elements such as shafts, gears, planet carriers, housings, clutches or their individual elements, housings and other suitable machine elements that are suitable for absorbing or delivering power or transmitting or supporting torques.

• - die Rotorwelle der Antriebsmaschine der erste Ausgang ist. Die Antriebsmaschine ist dementsprechend eine elektrische Maschine.
• - das erste Sonnenrad mit dem ersten Eingang wirkverbunden ist und mit den ersten Planetenrädern im Zahneingriff steht. Der erste Eingang ist beispielsweise eine Eingangswelle des ersten Planetentriebes oder ist der Schaft des Sonnenrades bzw. ist das Sonnenrad selbst.
• - der erste Planetenträger mit dem zweiten Ausgang Drehmomente übertragend wirkverbunden ist. Der zweite Ausgang ist beispielsweise eine mit dem ersten Planetenträger verbundene Welle oder der Planetenträger selbst.
• - Das Sonnenrad ist wahlweise über eine Welle oder ein Zwischenstück mit der Rotorwelle der Antriebsmaschine und dabei Drehmomente übertragend drehstarr verbunden. Alternativ wird eine Verbindung zwischen der Antriebsmaschine und dem Sonnenrad durch wenigstens eine Kupplung wiederholt ein- bzw. ausrückbar. Wahlweise sitzt das Sonnenrad beispielsweise direkt auf/an der Rotorwelle der Antriebsmaschine.
• - Weitere Ausgestaltungen der Erfindung sind nachfolgend aufgeführt, stehen jede für sich als Ausgestaltung der Erfindung oder können mit den bisherigen angeführten Merkmalen und auch untereinander beliebig miteinander kombiniert werden:
• - Die Kupplung ist auch als Bremse einsetzbar bzw. ist eine Bremse. Sie ist eine Trenneinheit und Schließeinheit alternativ Abbremseinheit und wahlweise mittels einer mechanischen, magnetischen oder hydraulischen Betätigung aktiviert.
• - Die Kupplung arbeitet wahlweise nach Prinzipien des Reibschlusses, Formschlusses und oder Kraftschlusses.
• - Die Kupplung ist eine Lamellenkupplung. So ist es denkbar, dass die Lamellenkupplung aus äußeren Lamellen und inneren Lamellen gebildet ist, welche abwechselnd axial aufeinanderfolgend angeordnet sind und welche beim Einrücken der Kupplung axial reibschlüssig gegeneinander geschoben werden. Die äußeren Lamellen sind axial verschiebbar aber in Umfangsrichtung um die Rotationsachse Drehmomente übertragend mit dem Gehäuse verbunden. Die Inneren Lamellen sind Drehmomente übertragend aber axial verschiebbar mit dem Hohlrad gekoppelt.
• - Die Kupplung ist eine Klauenkupplung. Wenigstens ein drehmomentübertragender, mit dem Gehäuse gekoppelter Klauenring wird beim Einrücken der Kupplung formschlüssig mit einem an das Hohlrad gekoppelten Klauenring in Eingriff gebracht.
• - Die Kupplung ist mindestens ein Freilauf, welcher vorzugsweise schaltbar ist. Denkbare Ausführungen von Freiläufen sind in diesem Falle Klemmkörper- oder Klemmrollenfreiläufe.
• - Der erste Planetenträger sitzt mit einem ersten Bund auf einem zweiten Bund des Differenzialkorbs, dabei sind die Bunde axial ineinandergesteckt, wobei vorzugsweise der erste Bund außen auf dem zweiten Bund sitzt.
• - Das Sonnenrad ist mittels eines Wälzlagers entweder in dem ersten Bund oder in dem zweiten Bund radial abgestützt.
• - Konzentrisch ineinander angeordnet sind zumindest Teile der Kupplung, des Hohlrades, der erste Bund und der zweite Bund, wenigstens ein Wälzlager und ein Wellenabschnitt des Sonnenrades.
• - Das Differenzial ist ein sogenanntes Stirnraddifferenzial. Es ist also ein Planetengetriebe, dessen Ausgleichsräder Planetenräder sind.

Embodiments of the invention provide that:

• - the rotor shaft of the prime mover is the first output. Accordingly, the drive machine is an electrical machine.
• - The first sun gear is operatively connected to the first input and meshes with the first planetary gears. The first input is, for example, an input shaft of the first planetary gear or is the shaft of the sun gear or is the sun gear itself.
• - The first planetary carrier is operatively connected to the second output in a torque-transmitting manner. The second output is, for example, a shaft connected to the first planet carrier or the planet carrier itself.
• - The sun gear is optionally connected to the rotor shaft of the drive machine via a shaft or an intermediate piece, thereby transmitting torque in a torsionally rigid manner. Alternatively, a connection between the prime mover and the sun gear can be repeatedly engaged or disengaged by at least one clutch. Optionally, the sun gear sits directly on/on the rotor shaft of the drive machine.
• - Further embodiments of the invention are listed below, each stand alone as an embodiment of the invention or can be combined with the features mentioned above and with each other as desired:
• - The clutch can also be used as a brake or is a brake. It is a separating unit and closing unit, alternatively a braking unit, and can be activated by means of a mechanical, magnetic or hydraulic actuation.
• - The clutch works either according to the principles of frictional locking, positive locking and/or force locking.
• - The clutch is a multi-plate clutch. So it is conceivable that the multi-plate clutch is formed from outer plates and inner plates, which are arranged alternately axially one after the other and which are pushed axially frictionally against each other when the clutch is engaged. The outer disks are connected to the housing so that they can be displaced axially but transmit torque in the circumferential direction about the axis of rotation. The inner plates transmit torque but are coupled to the ring gear so that they can be moved axially.
• - The clutch is a dog clutch. At least one torque-transmitting jaw ring coupled to the housing is positively engaged with a jaw ring coupled to the ring gear when the clutch is engaged.
• - The clutch is at least one freewheel, which is preferably switchable. In this case, conceivable versions of freewheels are sprag or roller freewheels.
• - The first planetary carrier sits with a first collar on a second collar of the differential cage, while the collars are inserted into one another axially, with the first collar preferably sitting on the outside of the second collar.
• - The sun gear is supported radially by means of a roller bearing either in the first collar or in the second collar.
• - Arranged concentrically one inside the other are at least parts of the clutch, the ring gear, the first collar and the second collar, at least one roller bearing and a shaft section of the sun gear.
• - The differential is a so-called spur gear differential. It is therefore a planetary gear whose differential gears are planetary gears.

One embodiment of the invention provides that a second operative connection is formed between the differential and the stationary locking device.

Such an active connection can advantageously be made very robust. The housing of the differential, which is preferably a planet carrier, advantageously offers many options for integrating or fastening elements of the locking device (parking lock). The elements referred to as snap-in holders can, for example, be stamped as simple snap-in toothing during chipless production of the differential housing or introduced into the casting mold of a corresponding planetary carrier. Simple levers and pawls or bolts can be used as mechanical locking devices, which can be produced inexpensively and designed to be very robust. The number of moving parts can be kept to a minimum. In addition, such an arrangement is designed to save installation space when viewed in terms of the dimensions of the transmission.

The operative connection formed between the differential and the locking device is a repeatedly releasable positive and/or frictional connection between the differential and the locking device, with which the differential is fixed in place relative to the environment, i.e. fixed in place relative to the vehicle or a housing.

The locking device is held stationary at least in the engaged state, with forces or torques initialized by the differential being able to be supported in a stationary manner. The term "stationary" stands for a fixed connection or support in the direction of rotation, optionally to a housing of the drive device, a housing of the transmission or any other housing, with the differential, i.e. the basket with the differential gears, rotating about its central axis relative to this housing is rotatably arranged. The central axis of the differential is the axis of rotation around which the differential cage rotates. Irrespective of this, the housing can also be movable or is fixed, for example, to the chassis or the body of a vehicle. The housing itself can also be moved, e.g. designed to travel with the vehicle.

The locking device can be designed to act mechanically and/or electrically and/or hydraulically and function by friction and/or positive locking or electromagnetically.

If a mechanically acting locking device is used, one embodiment of the invention provides that locking holders are provided on the differential cage for engaging at least one pawl of the locking device. Snap-in holders are undercut-like projections or depressions in the form of perforations or teeth, projections, grids or similar snap-in contours for a pawl, which are suitable for a repeatedly releasable positive connection between the pawl(s) and the snap-in contour. It is conceivable, for example, that the locking contour is designed as a locking toothing directly integrally on the differential cage or on one or more rings, wheels, plates or the like, which are positively, non-positively and/or cohesively connected are connected to the planet carrier or differential cage. One embodiment of the invention provides that the locking holders are formed on a side of the differential cage that faces away from the first planetary drive. This can be on the outer circumference, but also on the front. The above-mentioned elements or arrangements can be produced easily and inexpensively and with a robust design with regard to the above-mentioned exemplary embodiments without much effort.

All elements are provided as pawls which engage in the latch holder and/or engage behind it and are suitable for forming a repeatedly holding and detachable form-fitting connection between the housing and the differential cage. These can be designed as projections on levers or slides, can be resiliently prestressed, and are, for example, balls or pistons, discs or other mechanical components.

The planet carrier of the planetary drive and the planet carrier of the differential designed as a spur gear differential can be designed in one piece as a unit and, specifically in this case, preferably as a cast or injection molded part. In this sense, a spur gear differential is a differential with differential gears, which are designed as planet gears and are mounted on a planet carrier so that they can rotate around their own axis. Depending on the design, the output gears of the differential are ring gears or sun gears and optionally also the planet carrier in a power split. However, the preferred variant of the spur gear differential is symmetrical, i.e. the differential gears are two sun gears with the same or almost the same number of teeth. Two sets of compensating planet gears are provided, preferably having the same or approximately the same number of teeth. One set of planetary gears meshes with one sun gear (output gear) and the other set of planetary gears meshes with the other sun gear. In addition, a planetary gear of one compensation set is also in meshing engagement with a planetary gear of the other compensation set.

As already explained above, a preferred embodiment of the invention provides that the differential has a differential cage designed as a second planetary carrier of the differential designed as a spur gear differential. In this case, the first planetary carrier and the second planetary carrier are formed separately from one another, but are connected to one another. The advantage of such a configuration is that the planet carrier of the planetary drive and the planet carrier (differential cage) of the differential can be made of sheet metal. The load-bearing components of the respective planet carrier, such as the carrier cheeks and their connection, can preferably be produced simply and inexpensively without cutting and in turn preferably by cold forming such as drawing, stamping and embossing. A combination of sheet metal components, for example with cast or forged parts or components produced by cutting, is also conceivable.

character list

• 1 zeigt eine Antriebsvorrichtung 1, die mittels eines schematisch dargestellten Wirkprinzips und Grundaufbaus, in einer Ansicht längs entlang einer Zentralachse 31 der Antriebsvorrichtung 1.
• 2 zeigt ein Ausführungsbeispiel eines Getriebes 3 der Antriebsvorrichtung 1, welchem der mit 1 skizzierte Grundaufbau und Wirkprinzip zugrunde liegt.

The invention is explained in more detail below using exemplary embodiments.

• 1 shows a drive device 1, which by means of a schematically illustrated operating principle and basic structure, in a view along a central axis 31 of the drive device 1.
• 2 shows an embodiment of a transmission 3 of the drive device 1, which with 1 outlined basic structure and operating principle.

1 - The drive device 1 has various assemblies, such as a prime mover 2, a gear 3, a locking device 5, a clutch 6 and a housing 16. The drive machine 2 is an electric motor EM with a first output 7 which is formed by a rotor shaft 20 . The first output 7 is connected to a first input 8 of the transmission 3 . The gear 3 is formed from a planetary gear 11 and a differential 4 .

The first input 8 is the input to the planetary gear 11 and is connected in a torsionally rigid manner by an input shaft/sun shaft 32 and to the rotor shaft 20, e.g. via splines.

A second output 9, in this case an output of the planetary drive 11, is torsionally rigid and therefore torque-transmitting to a second input 10, in this case to the input of the differential 4, operatively connected.

The planetary drive 11 has a stepped planetary gear set 12, a first planetary carrier 13, a first sun gear 14 and a ring gear 15. The first sun gear 14 sits on the sun shaft 32. The stepped planetary gearset 12 is formed by stepped planets 17, of which due to the form of representation 1 only one is visible. Each stepped planet 17 consists of a first planetary gear 18 and a second planetary gear 19. The first planetary gears 18 and second planetary gears 19 are connected to one another in a torsionally rigid manner. The first planet gears 18 are larger in diameter and have a larger number of teeth than the second planetary gears 19 of the same stepped planetary gear 17. The torsionally rigid connection between one planetary gear 18 and the planetary gear 19 each results in a double planetary gear with two planetary gears 18 and 19. From the difference in diameter, i.e. a "gradation" of the diameter of the planetary gear 18 with the large diameter to that with the planet gear with the smaller diameter, the term "stepped planet" is derived.

The first sun gear 14 meshes with the planetary gears 18. The planetary gears 19 with the smaller diameter mesh with the ring gear 15.

Gear engagements are the meshing engagements of the teeth of the toothed gear elements listed above and below, which lead to the transmission of torque in the gear - such as the meshing of the outer teeth of a planetary gear with the outer teeth of a sun gear or the meshing of the outer teeth of a planetary gear with the internal toothing of the ring gear or the engagement of the compensating planetary gear in another compensating planetary gear or in a sun gear.

The differential 4 is a spur gear differential 30 which has a second planetary carrier 25 designed as a differential carrier, a set of first compensating planetary gears 33 and a set of second compensating planetary gears 34 , and a second sun gear 35 and a third sun gear 36 . Due to the form of representation, only one of the first and second compensating planet gears 33 and 34 is shown in a highly schematic manner. Each of the first compensating planetary gears 33 meshes with a second compensating planetary gear 34. Each of the first compensating planetary gears 33 also meshes with the second sun gear 35. In addition, the second compensating planetary gears 34 each mesh with the third sun gear 36. The second sun gear 35 is in this case an output gear of the spur gear differential 30 connected to an output shaft 37. The output shaft 37 runs axially in the direction of the axis of rotation 22 through the input shaft/sun shaft 32 designed as hollow shafts and through the rotor shaft 20 and is coupled to a drive wheel (not shown). In the drive device 1 shown, the third sun gear 36 is an output gear of the spur gear differential 30 and is connected to an output shaft 38 . The latter leads to another drive wheel, not shown, of the vehicle axle.

The first planetary carrier 13 of the first planetary drive is the second output 9, i.e. the output of the planetary drive 11. The second planetary carrier 25 is seated in a torsionally rigid manner on the first planetary carrier or alternatively is connected in a torsionally rigid manner to the second output 9 via a shaft (not shown).

The rotor shaft 20, the input shaft/sun shaft, the sun gears 14, 35 and 36, the planet carriers 13 and 25 and the ring gear 15 are arranged coaxially on the axis of rotation 22, which is the axis of rotation and central axis 31 of the drive device designed in a coaxial arrangement of its structural stages.

The axis of rotation or central axis 31 is considered to be oriented axially, regardless of its actual position in space. Accordingly, radial is perpendicular or transverse to the central axis 31.

The housing 16 of the transmission has individual housing sections 16a, 16b and 16c, which either form independent housings or, as is symbolized, are screwed together as housing sections 16a, 16b and 16c. It is also conceivable that the housing 16 is designed in one piece, in two parts or in more than three parts.

The ring gear 15, the first planetary carrier 13 and the second planetary carrier 25 are rotatable about the axis of rotation and relative to the housing 16 in the housing 16, which in this case is considered to be stationary relative to the differential carrier 21. The clutch 6 is arranged on the outer circumference of the ring gear 15 and concentrically to the axis of rotation 22 . Between the ring gear 15 and the housing 16, a repeatedly switchable first operative connection W1 is formed via the clutch 6 in such a way that the ring gear 15 is fixed relative to the housing section 16b by engaging the clutch 6 and is therefore no longer rotatable and can be engaged again by disengaging the clutch 6 relative to the housing 16 is rotatable.

A second operative connection W2 is formed between the differential 4 and the stationary locking device 5, for which latch holders 26 are provided on the differential cage 21 for engaging at least one pawl 29 of a parking lock or the locking device 5, which is otherwise not shown in detail. The pawl 29 is pivoted to the housing portion 16c but otherwise held in place by the housing 16 and is engageable with the latching brackets 26. As shown in FIG. The locking holders 26 are, for example, teeth of a locking toothing formed on the second planetary carrier 25, in the gaps of which the locking pawl 29 can engage in a form-fitting manner. Alternatively, the locking holders are also formed on a ratchet wheel or the like that is formed separately from the planetary carrier and is connected to the differential cage in a rotationally fixed manner about the axis of rotation.

In 1 are marked with V1, V2, V3 or V4 perpendicularly penetrated by the central axis/rotational axis 31 and hereinafter referred to as toothing planes V1, V2, V3 or V4 radial planes. It is assumed that the contacts of the teeth of the individual meshings of the spur gears of either the planet gears 18, 19, 33 or 34 with the respective sun gear 14, 35, 36 or ring gear 15 ideally in the axial direction in the middle of the effective (effective) width of the respective Gears lie and that this gear plane V1, V2, V3 or V4 halves the respective effective tooth widths, ie run through an assumed axially central tooth engagement. There are the teeth of the first sun wheel 14 and the large planet wheel 18 of the stepped planet 17 in the first toothing plane V1. In the gearing level V2, the gearing of the second planetary gears 19 of the stepped planetary gears 17 meshes with the gearing of the ring gear 15. In the third gearing level V3, the gearing of the first compensating planetary gears 33 with the second sun gear 35 and each of the compensating planetary gears 33 with the gearing of one of the second compensating planetary gears 34 in meshing engagement. In the fourth gearing plane V4, the gearing of the second planetary gear wheel 34 is in meshing engagement with the gearing of the third sun gear 36. Deviating from the previously mentioned assumption for the meshing of the teeth of the second compensating planetary gears 34, the result is that the toothing plane V4 runs centrally through the effective tooth width of the third sun gear 36, but at the respective compensating planetary gear 34 it runs by a quarter of the effective tooth width to the right compared to the center in the figure is offset outside. Accordingly, the third toothing plane V3 also runs offset by a quarter of the effective tooth width in the image to the left in relation to the center of the effective tooth width of the compensating planet gears 34 . The toothing of the respective second compensating planet wheel 34 is therefore effectively effective in the two toothing planes V3 and V4. It follows that the effective tooth width of the third sun gear 36 is half or less of the effective tooth width of the second differential planetary gears 34 and that the effective tooth width of the second differential planetary gears 34 is wider than the effective tooth width of the first differential planetary gears 33 and than that of the second sun gear 35 .

The first planetary carrier 13 is rotatably mounted about the axis of rotation 22 at the bearing point L1 on the housing section 16a or on a bearing plate 39 of the electric motor EM that is firmly supported with respect to the housing section 16a. The first sun gear 14 and the second planet carrier 25 (differential carrier 21) are mounted against one another at the bearing point L2. At the third bearing point L3, the differential cage 21 is mounted on the housing section 16c such that it can rotate about the axis of rotation 22 on the parking lock side.

2 - The gear 3 is shown in a longitudinal section along the axis of rotation 22. As already described above, the planetary drive 11 is provided with the stepped planetary gearset 12 , the first planet carrier 13 , the first sun gear 14 and the ring gear 15 . The first sun gear 14 has to be seated on the sun shaft 32 (see 1 ) inside an internal toothing 40 or a similar spline profile. The toothing 41 of the respective first planet wheel 18 of the respective step planet 17 is in the toothing plane V1 with the toothing 42 of the sun wheel 14 in meshing engagement. The teeth 43 of the second planet wheels 19 are in the second toothing plane V2 with the inner teeth 44 of the ring gear 15 in meshing engagement. The first planet gears 18 are larger in diameter and have a larger number of teeth than the second planet gears 19 of the same stepped planet 17.

The first planet carrier 13 is formed from a first carrier cheek 59, a second carrier cheek 61 and a plurality of planet bolts 53 corresponding in number to those of the planet gears 18 and 19, respectively. A section 52 of the first planet carrier 13 is provided with a hub 57 centered concentrically to the axis of rotation 22 .

The differential 4 is a spur gear differential 30 which has the second planetary carrier 25 designed as a differential carrier 21 , the set of first compensating planetary gears 33 and the set of second compensating planetary gears 34 , the second sun gear 35 and the third sun gear 36 .

The second planet carrier 25 consists of a first carrier cheek 58 and a second carrier cheek 62 which form the differential carrier 21 . A section 51 of the second planet carrier 25 is provided with a hub 56 aligned concentrically to the axis of rotation 22 .

Due to the form of representation, only one of the first compensating planet gears 33 is shown. The first differential planetary gears 33 are so wide that they extend axially beyond the third and fourth gear levels V3 and V4. The second compensating planetary gears 34 are covered by the first compensating planetary gears 33 in this representation and only indicated with a dashed line. The axial width of the first compensating planetary gears 33 corresponds to at least twice the width of the toothing of the second sun gear 35, the axial width of the second compensating planetary gears 34 corresponding to the width of the third sun gear 36. The first Compensating planetary gears 33 and the second compensating planetary gears 34 are, as shown with reference to the first compensating planetary gears 33, mounted on the left and right with pins 45 in the planet carrier 25 or are alternatively mounted on planet bolts (not shown), which in turn are supported on the left and right in the planet carrier.

For a better understanding of alternative configurations of the arrangements of the differential gears and their meshing, reference is once again made to the representation in FIG 1 taken. There the toothing of the first compensating planetary gears 33 with the second sun gear 35 and each of the first compensating planetary gears 33 with the toothing of one of the second compensating planetary gears 34 in the third toothing plane V3 mesh with one another, so that in the fourth toothing plane V4 the teeth of the second compensating planetary gears 34 with the toothing of the third sun gear 36 are in meshing engagement. In the with 2 In contrast to the embodiment shown, the first compensating planetary gears 33 mesh with the second sun gear 35 in the third toothing plane V3 and the second compensating planetary gears 34 mesh with the third sun gear 36 and the first compensating planetary gears 33 in the fourth toothing plane V4 Toothing 48 of the third sun wheel 36 is axially wider than the toothing 47 of the second sun wheel 35.

This results in the spur gear differential considered with two imaginary radial toothing planes running through the differential, that optionally in one of the toothing planes the differential planetary gears of one set mesh with one differential planetary gear of the other set and at the same time with one of the sun gears, while in the other Gearing level the differential gears of the other set (only) mesh with the other of the sun gears.

For the meshing of the teeth of the second compensating planetary gears 34, the toothing plane V4 runs centrally through the effective tooth width of the third sun gear 36, but at the respective first compensating planetary gear 33 it is offset to the right by a quarter of the effective tooth width compared to the center in the figure. Accordingly, the third toothing plane V3 also runs offset by a quarter of the effective tooth width in the image to the left in relation to the center of the effective tooth width of the first compensating planet gears 33 . The toothing of the respective second compensating planet wheel 34 is therefore effectively effective in the two toothing planes V3 and V4. As a result, the effective tooth width of the second sun gear 35 corresponds to half or less of the effective tooth width of the first differential planetary gears 33 . The first and second differential planetary gears 33 and 34 have the same number of teeth compared to each other. The second sun gear 35 and the third sun gear 36 have the same number of teeth as compared to one another. So that the tooth profiles do not overlap in the radial direction and thus, for example, the first compensating planet gears 33 do not collide with the teeth 48 of the third sun gear 36, the tooth heights of the teeth 47 and 48 of the sun gears 35 and 36 and the center distances of the The axes of rotation of the first and second compensating planetary gears 33 and 34 to the axis of rotation 22 with the same modules of the teeth from each other.

In the first planetary carrier 13 there is a roller bearing 49, which in this case is designed as a roller bearing or needle bearing, but can also be a ball bearing, tapered roller bearing or any other roller or plain bearing of any other design. About the roller bearing 49 is the planet carrier 13 as shown in FIG 1 rotatably mounted about the axis of rotation 22 at the bearing point L1 on the housing section 16a or on a bearing plate 39 of the electric motor EM that is firmly supported on the housing section 16a.

In the 1 bearing point L2 described is realized using another roller bearing 50, which in the with 2 illustrated embodiment is shown as a ball bearing. The first sun gear 14 and the second planetary carrier 25 (differential carrier 21) are mounted so as to be rotatable relative to one another about the axis of rotation 22 via this further roller bearing 50 . The toothing 42 of the first sun wheel 14 lies in the first toothing plane V1. An internal toothing 40 of the first sun gear 14 or a similar spline profile together with a corresponding profile on the sun shaft 32 (in 1 however not in 2 shown) results in a spline (general plug-in connection) axially between the first toothing level V1 and the second toothing level V2. It also follows that the internal toothing 40 is located axially between the toothing 42 of the first sun gear 14 and the bearing point L2 ( 1 ) or is arranged axially between the teeth 42 of the first sun gear 14 and the further roller bearing 50 .

The bearing center of the further roller bearing 50, which in this case is defined by a radial plane running through the ball centers of the balls of the ball bearing, lies in the second toothing plane V2. The other roller bearing 50 sits with an inner ring 55 radially on the outside on a shank 54 of the first sun wheel 14. A section of the shank 54 is cut through the toothing plane V2 - is therefore in the toothing plane V2. The roller bearing 50 is surrounded on the outside peripheral side by a first section 51 of the differential carrier 21 or the second planetary carrier 25 , which in turn is surrounded by a second section 52 of the first planetary carrier 13 .

The sections are designed as the hubs 56 and 57, from which the carrier cheeks 58 and 59 of the respective planetary carrier 13 and 25 extend. The hub 57 of the carrier cheek 59 of the first planetary carrier 13 is therefore directed axially inwards into the planetary carrier 13 in the direction of a further carrier cheek 61 of the first planetary carrier 13 and the hub 56 of the carrier cheek 58 of the second planetary carrier 25 is also directed into the planetary carrier 13 Direction of the other carrier cheek 61 of the first planetary carrier 13 directed. The result is that the hub 56 of the carrier cheek 58 of the second planetary carrier 25 is directed away from a further carrier cheek 62 of the second planetary carrier 25 and in the opposite direction to the axial alignment of a hub 63 of the further carrier cheek 62 of the second planetary carrier 25. Sections of both hubs 56 and 57 thus surround the roller bearing 50.

Around the circumference of the respective hub 56 and 57 of the first planetary carrier 13 and second planetary carrier 25, the second planetary gears 19 are distributed in the second toothing plane V2, which together with the first planetary gears 18 can each be rotated on a planetary bolt 53 about the axis of rotation of the stepped planetary gear 17 are stored. Ring gear 15 or its internal toothing 44 follows in the sequence from the axis of rotation 22 radially from the inside outwards onto the second planetary gears 19. The internal toothing 44 is in toothing plane V2 with the toothing 43 of the second planetary gears 19 in meshing engagement. Finally, ring gear 15 is surrounded by clutch 6 or brake 6, which is also intersected by second toothing plane V2.

• - Radial am weitesten innen im Planetengetriebe 11 ist ein Schaft des ersten Sonnenrades 14 angeordnet, auf welchem das Wälzlager 50 sitzt, wobei das Wälzlager 50 von einer Nabe 56 des zweiten Planetenträgers 25 (des Differenzialkorbs 21) umgeben ist.
• - Die Nabe 56 des zweiten Planetenträgers 25 wiederum ist radial von der Nabe 57 des ersten Planetenträgers 13 umgeben.
• - Umfangsseitig um die Nabe 57 des ersten Planetenträgers 13 außen herum sind die zweiten Planetenräder 19 bzw. ist deren Verzahnung 43 verteilt angeordnet.
• - Schließlich folgt radial außen die innere Verzahnung 44 des Hohlrades 15 und das Hohlrad 15 ist außen umfangsseitig zumindest von einem Abschnitt der Kupplung 6 bzw. Bremse umgeben.

In summary, the following constellation results:

• - Arranged radially innermost in the planetary gear 11 is a shank of the first sun gear 14 on which the roller bearing 50 sits, the roller bearing 50 being surrounded by a hub 56 of the second planet carrier 25 (of the differential carrier 21).
• - The hub 56 of the second planet carrier 25 in turn is radially surrounded by the hub 57 of the first planet carrier 13.
• The second planet gears 19 or their toothing 43 are distributed around the circumference of the hub 57 of the first planet carrier 13 .
• Finally, radially on the outside, the inner toothing 44 of the ring gear 15 follows, and the ring gear 15 is surrounded on the outside peripheral side by at least a portion of the clutch 6 or brake.

In this case, the second planet carrier 25 is designed as a cast part and has the carrier cheek 59 which is axially opposite to the carrier cheek 58 of the first planet carrier 13 or rests axially against it. The first planetary drive 11 and the differential 4 are axially nested with one another because the hub 56 extending axially from the carrier cheek 58 of the second planet carrier 25 dips axially into the planetary gear 11 in the direction of the planetary gear 11 in such a way that the section (the hub 57) extends axially into a space formed radially between the second planetary gears 19 and the axis of rotation 22 . In addition, the first planetary carrier 13 has the first carrier cheek 59, which is axially opposite to the second carrier cheek 58 or rests against it, and from which the hub 56 extends in such a way that it dips axially into the planetary gear 11 in the direction of the first planet wheel 18 . The hub 57 of the first carrier cheek 59 also protrudes axially into the space which is formed radially between the second planet gears 19 and the axis of rotation 22 . At least a section of the first hub 57 sits on the hub 56 of the second planetary carrier 25. Both hubs 56 and 57 are intersected by the second toothing plane V2.

The bearing with which the differential carrier 21 (second planetary carrier) as shown in FIG 1 at the third bearing point L3 on the parking lock side on the housing section 16c so as to be rotatable about the axis of rotation 22 is designed as a roller bearing 60 in the form of a ball bearing and in 2 pictured. The locking holders 26 of the parking lock are located axially between the bearing point L3 (see 1 ), in which with 2 illustrated case, distributed axially between the roller bearing 60 and the fourth toothing plane V4 on the second planetary carrier 25 about the axis of rotation 22 .

Reference List

1

drive device

2

prime mover

3

transmission

4

differential

5

locking device

6

coupling

7

first exit

8th

first entrance

9

second exit

10

second entrance

11

planetary drive

12

stepped planetary set

13

first planet carrier

14

first sun wheel

15

ring gear

16

Housing

16a

housing section

16b

housing section

16c

housing section

17

step planet

18

first planet wheel

19

second planet gear

20

rotor shaft

21

differential cage

22

axis of rotation

23

first teeth

24

second teeth

25

second planet carrier

26

snap holder

27

-

28

-

29

pawl

30

spur gear differential

31

Central axis/axis of rotation

32

Input shaft/sun shaft

33

first balancing planet wheel

34

second compensating planet wheel

35

second sun wheel

36

third sun wheel

37

output shaft

38

output shaft

39

bearing shield

40

internal teeth

41

Gearing of the first planet wheel

42

Gearing of the first sun gear

43

Gearing of the second planet wheel

44

internal toothing of the ring gear

45

cones

46

Gearing of the first compensating planet wheel

47

Gearing of the second sun wheel

48

Gearing of the third sun wheel

49

roller bearing

50

roller bearing

51

section of the differential cage

52

Section of the first planet carrier

53

planet bolt

54

Shaft of the first sun gear

55

inner ring

56

Hub of the second planet carrier

57

Hub of the first planet carrier

58

first carrier cheek of the second planet carrier

59

first carrier cheek of the first planet carrier

60

roller bearing

61

second carrier cheek of the first planet carrier

62

second carrier cheek of the second planet carrier

63

Hub of the second carrier cheek of the second planet carrier

EM

electric motor

w1

first active connection

W2

second active compound

L1

storage place

L2

storage place

L3

storage place

Claims (7)

Planetary drive (11) with a stepped planetary gearset (12), a first planetary carrier (13), a first sun gear (14), a ring gear (15) and a clutch (6), wherein - the stepped planetary gearset (12) consists of individual stepped planetary gears (17) - each of the stepped planetary gears (17) has a first planetary gear (18) and a second planetary gear (19) coaxially connected thereto in a torsionally rigid manner, - the ring gear (15) meshes with planetary gears (18, 19) of the stepped planetary gear set (12) is - between the ring gear (15) and the housing (16) via the clutch (6) a repeated switching bare first active connection (W1), - the clutch (6) surrounds at least a section of the ring gear (15) on the outer circumference, - a roller bearing (50) concentric to a common axis of rotation (22) of the ring gear (15), the sun gear (14 ) and the roller bearing (50), - the second planet gears (19) are distributed around the roller bearing (50) at a radial distance from the roller bearing (50) and mesh with the ring gear (15), - a second planet carrier ( 25) is rotatably mounted about the axis of rotation (22) by means of the roller bearing (50), - a differential (4) has the second planet carrier (25) with a first and a second carrier cheek (58, 62), - the first carrier cheek (58 ) of the second planet carrier (25) and the first carrier cheek of the first planet carrier (13) are fastened to one another and these two carrier cheeks (58, 59) are supported on the roller bearing (50). planetary drive claim 1 , wherein the first sun gear (14) is supported by the roller bearing (50). planetary drive claim 1 or 2 , wherein an imaginary toothing plane (V2) runs through the clutch (6), wherein the toothing plane (V2) is an imaginary radial plane pierced perpendicularly by the axis of rotation (22) of the ring gear (15), and wherein the toothing plane (V2) is in the middle of the effective width of a toothing (43) of at least two of the second planetary gears (19) through the second planetary gears (19). planetary drive claim 1 , 2 or 3 , wherein a toothing (42) of the sun gear (14) is arranged axially next to the roller bearing (50). planetary drive claim 3 , wherein the toothing plane (V2) runs radially through the roller bearing (50). Drive device (1) with a drive machine (2) and the planetary drive (11) according to any one of the preceding claims and as the differential (4) designed transmission (3), the clutch (6) and the housing (16), wherein - At least sections (51, 52) of the planet carriers (13, 25) are surrounded by the clutch (6); - The drive device (1) has a repeatedly switchable second operative connection (W2) with a locking device (5). Drive device (1) after claim 6 , which has a first operative connection (W1) between the planetary drive (11) and the housing (16) that can be repeatedly engaged and disengaged via the clutch (6) and a second operative connection (W2) that can be switched repeatedly via a locking device (5) between the second Planet carrier (25) and the housing (16).

Images