CN114207321B - Compact transmission device with multi-stage planetary gear set and spur gear differential - Google Patents

Compact transmission device with multi-stage planetary gear set and spur gear differential Download PDF

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Publication number
CN114207321B
CN114207321B CN202080055478.8A CN202080055478A CN114207321B CN 114207321 B CN114207321 B CN 114207321B CN 202080055478 A CN202080055478 A CN 202080055478A CN 114207321 B CN114207321 B CN 114207321B
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CN
China
Prior art keywords
planetary gear
differential
transmission device
gear set
spur
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CN202080055478.8A
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Chinese (zh)
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CN114207321A (en
Inventor
弗洛里安·赖因勒
约亨·洛菲尔曼
巴斯蒂安·鲁普
塞巴斯蒂安·朗汉斯
约尔格·鲍尔
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Schaeffler Technologies AG and Co KG
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Schaeffler Technologies AG and Co KG
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0806—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with a plurality of driving or driven shafts
    • F16H37/0813—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with a plurality of driving or driven shafts with only one input shaft
    • F16H37/082—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with a plurality of driving or driven shafts with only one input shaft and additional planetary reduction gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
    • F16H48/11—Differential gearings with gears having orbital motion with orbital spur gears having intermeshing planet gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/38—Constructional details
    • F16H48/40—Constructional details characterised by features of the rotating cases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/042—Guidance of lubricant
    • F16H57/0427—Guidance of lubricant on rotary parts, e.g. using baffles for collecting lubricant by centrifugal force
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0467—Elements of gearings to be lubricated, cooled or heated
    • F16H57/0469—Bearings or seals
    • F16H57/0471—Bearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0467—Elements of gearings to be lubricated, cooled or heated
    • F16H57/0479—Gears or bearings on planet carriers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/048—Type of gearings to be lubricated, cooled or heated
    • F16H57/0482—Gearings with gears having orbital motion
    • F16H57/0483—Axle or inter-axle differentials
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/048—Type of gearings to be lubricated, cooled or heated
    • F16H57/0482—Gearings with gears having orbital motion
    • F16H57/0486—Gearings with gears having orbital motion with fixed gear ratio
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H57/082—Planet carriers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K1/00—Arrangement or mounting of electrical propulsion units
    • B60K2001/001—Arrangement or mounting of electrical propulsion units one motor mounted on a propulsion axle for rotating right and left wheels of this axle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
    • F16H2048/104—Differential gearings with gears having orbital motion with orbital spur gears characterised by two ring gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
    • F16H2048/106—Differential gearings with gears having orbital motion with orbital spur gears characterised by two sun gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H48/00—Differential gearings
    • F16H48/38—Constructional details
    • F16H48/40—Constructional details characterised by features of the rotating cases
    • F16H2048/405—Constructional details characterised by features of the rotating cases characterised by features of the bearing of the rotating case
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H2057/085—Bearings for orbital gears

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)

Abstract

The invention relates to a transmission device (1) for a motor vehicle, comprising a multi-stage planetary gear set (2) and a spur gear differential (3) connected via a common planetary gear carrier (4), having a first and a second planetary gear set (6, 7) which mesh with one another in pairs, wherein each planetary gear set (6, 7) comprises a sun gear (13, 14) which is rotationally fixedly connected to an output shaft (15, 16) of the spur gear differential (3), torque introduced into the transmission device (1) via an input shaft is transmitted from the multi-stage planetary gear set (2) into the spur gear differential (3) and subsequently onto the output shaft (15, 16) for transmission onto driven wheels, wherein the engagement plane of the multi-stage planetary gear set (2) radially overlaps at least one sun gear (13, 14) of the spur gear (3), wherein a compensating gear peg (10, 11) of the multi-stage planetary gear set (2) is guided radially with respect to the sun gear (13, 14) via a bearing cap (12) and is fixed axially on the differential cap (12) via the differential cap (4) on the opposite axial bearing side (12) and via the differential cap (12), the floating bearing is obtained by the engagement of the teeth of an input sun gear (39) of a multi-stage planetary gear set (2) and a spur gear (17) forming a double planetary gear.

Description

Compact transmission device with multi-stage planetary gear set and spur gear differential
Technical Field
The application relates to a transmission device for a motor vehicle, comprising a multi-stage planetary gear set and a spur gear differential connected via a common carrier.
Background
DE 10 2015 214 031 A1 shows a transmission device for a motor vehicle, which comprises a transmission input stage and a differential connected thereto via a common planetary carrier. The differential, which is configured as a spur differential, has two planetary gear sets, the planetary gears of which mesh with separate sun gears. In addition, the two planetary gear sets of the differential are in meshing engagement with each other in pairs. The transmission input stage has a drive sun gear which meshes with a first planetary gear set which is connected in a rotationally fixed manner to a second planetary gear set.
A transmission device associated with an electric drive unit is known from EP 2 821 672 A1, comprising a rotor shaft as an input shaft and a differential and a multi-stage planetary gear set, also called transmission input stage, which is designed as a planetary transmission, the sun gear of which is associated with the input shaft. The differential, which is configured as a spur differential, comprises planetary gears as compensating wheels and sun gears as driven wheels, wherein each sun gear is associated with an output shaft. The torque introduced via the input shaft is introduced into the spur gear differential via the multi-stage planetary gear set and from there transmitted to the output shaft and subsequently to the driven wheels. The input shafts form hollow shafts through which one of the output shafts is guided.
Disclosure of Invention
The invention is based on the object of providing a transmission device for a drive device which is compact at least in the axial direction, which can be installed in a simple manner and which can be realized in a cost-effective manner.
According to the invention, it is proposed that the planet pins of the multi-stage planetary gear set are arranged with radial spacing relative to the sun gear thereof through the meshing plane of the spur gear differential, and that the compensating pins further radially and axially fix the differential cover at the end facing away from the multi-stage planet gears. In order to support the planetary gear carrier, it is proposed that the planetary gear carrier is supported on the drive side of the transmission device via the running gear of the large planetary gear as a floating bearing and on the opposite side via a differential cover via a fixed bearing in the housing of the transmission device.
Thanks to the concept according to the invention comprising an axial expansion of the spur gear differential, an axially compact spur gear differential can advantageously be achieved, which simultaneously positively influences the required installation space of the entire transmission device. Due to the spur differential which expands in the radial direction, a radial overlap occurs at least between the engagement planes of the multi-stage planetary gear set and the spur differential. In order to achieve the solution, the planet pins of the multi-stage planetary gear set are axially elongated, so that they enable guiding and fixing of the differential cover. Advantageously, the compact concept according to the invention results in a desired small deformation of the planet carrier, which positively influences the torsional rigidity of the transmission device.
Furthermore, the compact design according to the invention makes it possible to implement alternative, cost-effective production methods for the individual components of the transmission device, such as cold forming methods, for example deep drawing, stamping or extrusion, which ensure an improved overall rigidity even with reduced wall thicknesses.
The bearing arrangement of the planetary gear carrier, which is constructed according to the invention, comprises a floating bearing on the drive side, which is obtained by the meshing engagement of the large double planetary gear with the input sun gear. On the output side, the differential cover, which is connected to the planetary carrier in a rotationally fixed manner, is preferably mounted in the transmission housing of the transmission device via a fixed bearing in the form of a deep-groove ball bearing.
In an advantageous embodiment, which is based on an axially compact design of the transmission device, the sun gear of the spur gear differential is arranged close to the planet carrier. In order to achieve the smallest possible axial distance, recesses are introduced in the guide support structure of the planet gear carrier, in each case locally close to the compensating wheel pins, which recesses enable an unobstructed rotation of the sun gear.
A preferred embodiment of the spur gear differential provides that the outer envelope circle of the spur gear differential is designed to be smaller than the tip circle of the internal toothing of the associated ring gear. By means of this measure, a simplified assembly sequence occurs, since the engagement of the ring gear is canceled before the spur gear differential is assembled via the planet gears.
According to the invention, the compensating wheel pin of the spur gear differential is fixed in the installed state in a form-fitting manner axially via the component geometry of the differential cover and of the planetary gear carrier. Preferably, the compensating wheel pin is inserted by one end into a blind hole of the planetary gear carrier and by the other end into a hole of the differential cover and is supported at the radially inward edge of the differential cover. For cost reasons, additional positive and/or material-locking rotational stops can be dispensed with.
The durable positioning of the planetary gear bolts of the multi-stage planetary gear set is carried out by means of the pressure-contact connection at the two soft ends of the planetary gear bolts. The crimp of the planetary gear bolts produces a play-free fastening at the differential cover and the planetary gear carrier, which does not require a complementary press fit of the bolts in the planetary gear carrier.
The crimp causes a durable connection which is also subject to high mechanical demands, such as vibrations which occur, for example, in the operating state of the transmission device.
For crimping the planetary gear pin, a crimping tool is preferably used, which has a special contour, which first has an acute angle, which is then formed more gradually, whereby the deformation increases simultaneously with an increasing axial crimping path. By means of this measure, the loadability of the crimp can be increased while the crimping force remains unchanged. The crimp of the planetary gear bolts, which is also referred to as a crimp mark, furthermore leads to an improved torsional rigidity of the planetary gear carrier, which positively influences the support of the planetary gears, for example, reducing the meshing forces of the gears and thus optimizing the service life of the entire transmission device.
The multi-stage planetary gear set is free, wherein the planetary gears, which are also referred to as spur gears, are supported via rolling bearings in the form of needle rollers. Here, all the planet gears are centered via the planet gear pins and the needle roller ring. The release of the planetary gear set required for load compensation takes place via the associated ring gear. For spur gears of a multistage planetary gear set, also referred to as drive teeth, which are each associated with a planetary gear set, an axial distance of at least 6mm is provided for cost-effective production.
The transmission device comprises a lubrication system, wherein the associated compensating wheel pin has a blind bore or a longitudinal bore closed on one side in a mounting-related manner for the targeted lubrication of a rotatably mounted compensating wheel or spur gear of a spur gear differential and of a multi-stage planetary gear set. Preferably, the oil pan is inserted at the end side into a compensating gear bolt of the spur gear differential. The oil or oil mist is accommodated in the transmission device in the operating state by centrifugal force via an oil sump, which is also referred to as a guide plate, preferably connected around all the planetary gear bolts, and is then guided into the longitudinal bores and from there fed to the bearing device via the radial bores of the planetary gear bolts.
The planet pins associated with the multi-stage planetary gear set preferably form a dividing wall centrally in the longitudinal bore to form a blind bore so that incoming lubricating oil can then flow via the radial bore to the axially offset bearings of the spur gears.
Preferably, to manufacture the teeth of the multi-stage planetary gear set and/or the spur differential, a strong scraping tooth is suitable. Strong scraping teeth are a method for continuous cutting processing for manufacturing tooth portions. The production process combines rolling milling and collision by continuous rolling by axial feed, and enables production of internal and external teeth. The proposed strong scraping tooth enables a higher cross angle with a larger distance, whereby tool wear and thus costs can be reduced. In order to achieve an overall cost-effective production, the teeth of the multi-stage planetary gear set are preferably arranged axially at a distance of at least 6mm from one another.
The transmission device according to the invention, which is constructed compactly and comprises a spur gear differential and a multistage planetary gear set, is preferably suitable for a drive train of an electric drive unit of a motor vehicle. For example, it is suitable to couple the transmission device with an electric motor in order to form a so-called E axle. E-axle is a solution for electric drive or hybrid applications of electric-only vehicles. In the case of E axles, components, such as motor, axle and transmission, are combined into a structural unit, which components are used separately in a conventional manner.
Drawings
The invention is described in detail below on the basis of embodiments shown in the three figures. The invention is not limited to the embodiments shown. The drawings show:
FIG. 1 illustrates a longitudinal cross-section of a transmission device constructed in accordance with the present invention including a spur gear differential and a multi-stage planetary gear set;
FIG. 2 illustrates a partial three-dimensional view of a spur differential and a multi-stage planetary gear set of the transmission device according to FIG. 1;
FIG. 3 shows a front view of the gears of the planetary gear set of the spur gear differential and of the multi-stage planetary gear set;
Fig. 4 shows a detailed view of the spur differential through the transmission device.
Detailed Description
The following description of the drawings of the embodiments applies to a better understanding of the present invention. Here, identical components are provided with identical reference numerals.
In fig. 1, the construction and arrangement of the individual components of a transmission device 1 according to a preferred embodiment is depicted, wherein not all components of the transmission device 1 are shown in fig. 1. The transmission device 1, which is associated with a powertrain (not shown) of an electric drive of a motor vehicle, for example, is divided into a multistage planetary gear set 2 and a spur gear differential 3. In a multistage planetary gear set 2, also referred to as a transmission section or a reduction stage, the drive torque, which is introduced by an E-motor (not shown), for example, is converted or reduced from a high input rotational speed to a low output rotational speed. The output torque achieved is then distributed via the spur gear differential 3 to its output shaft which is connected to the drive wheels of the motor vehicle. For the multi-stage planetary gear set 2 and the spur differential 3, a planetary carrier 4 is provided, which is inserted into a housing 5 of the transmission device 1.
The planet carrier 4 is rotatably mounted on the drive side via a meshing engagement between an input sun gear 39, which surrounds the output shaft 15, and the large planet gears 17, which is designed, for example, as a floating bearing 34. The driven side of the carrier 4 is supported via a fixed bearing 36. For this purpose, a deep groove ball bearing is provided, which is inserted between the receptacle 37 of the transmission housing 5 of the transmission device 1 and a cylindrical, axially projecting shoulder 38 of the differential cover 12, which is connected to the planet carrier 4 in a torsionally rigid manner.
As shown in fig. 2, the spur gear differential 3 comprises two planetary gear sets 6,7 with differently dimensioned compensating wheels, namely a wide compensating wheel 8 and a narrow compensating wheel 9, which are each rotatably mounted on an associated compensating wheel pin 10, 11, which is inserted in a rotationally fixed manner into an associated bore of the planetary gear carrier 4 and of the differential cover 12. Radially inward, the compensating wheels 8, 9 mesh with the sun wheels 13, 14, respectively, wherein each sun wheel 13, 14 is connected rotationally fixed to an output shaft 15, 16.
The multistage planetary gear set 2 comprises transmission gears, wherein two spur gears 17, 18, which are axially offset, have oblique teeth and are connected to one another and are also referred to as planetary gears, are rotatably mounted on a planetary gear peg 21 via rolling bearings 19, 20, said spur gears being in engagement with further gears (not shown). The rolling bearings 19, 20 are preferably needle roller rings (KZK). For cost-effective production, two spur gears 17, 18 of different sizes, which are offset from one another, are arranged at an axial distance of 6mm or more. In addition, the multi-stage planetary gear set 2 or its planetary gear set 21 overlaps the sun gears 13, 14 and thus the meshing plane of the spur gear differential 3 in the installed state. Focusing on the axially compact design of the transmission device 1, the meshing plane of the sun gear 13 of the spur gear differential 3 is arranged axially close to the planet carrier 4. In order to achieve the smallest possible axial distance, recesses 33 for sun wheel 13 are introduced locally into the guide support structure of planet carrier 4.
The durable position fixing of the planetary gear bolts 21 of the multi-stage planetary gear set 2 is carried out by means of crimping portions 22, 23 at the two soft ends of the planetary gear bolts 21. The pressure-contact points 22, 23 are advantageously arranged distributed over the circumference of the planetary gear bolt 21, whereby the planetary gear bolt 21 is connected and rotationally fixed and fixedly secured to the differential cover 12 or the planetary gear carrier 4 in a force-and/or form-fitting manner. In order to lubricate the rolling bearings 19, 20 of the spur gears 17, 18 of the multi-stage planetary gear set 2, a blind bore 24 is introduced into the planetary gear bolt 21, into which, in the operating state 1, from the side oriented toward the output shaft 16, the lubricating oil flows and via radial bores 25 of the planetary gear bolt 21 into an annular space 26 axially delimited by the rolling bearings 19, 20.
Fig. 2 and 3 illustrate the arrangement or installation position of the planetary gear sets 6, 7 of the spur gear differential 3 and the spur gears 17, 18 of the multi-stage planetary gear set 2 forming the gear train, also referred to as double planetary gears, in different views in order to achieve a transmission device 1 that is compact in the axial direction. In fig. 2, the planet pins 21 of the multi-stage planetary gearset 2, which lead through the engagement plane of the spur differential 3, extend radially at a distance from the sun gears 13, 14 of the spur differential 3.
In the detail section of the transmission device 1 according to fig. 4, the installation position of the compensating wheel pin 10 and the lubrication of the compensating wheels 8, 9 of the spur gear differential 3 are shown in particular. In the installed state, the compensating wheel pin 10 is inserted into a blind hole 27 of the planet wheel carrier 4 and is fixed axially on opposite sides at a radially inward edge 28 of the differential cover 12. In order to load the bearing 29 of the compensating wheel 8, which is designed as a sliding bearing, with lubricating oil in a targeted manner, an oil pan 31 is inserted at the end into a longitudinal bore 30 of the compensating wheel pin 10. The lubricating oil received by the oil pan 31 is guided into the longitudinal bore 30, which is subsequently fed to the bearing 29 via the radial bores 32 of the planetary bolts 10.
Description of the reference numerals
1 The transmission device 2 is provided with a multistage planetary gear set 3, a spur gear differential mechanism 4, a planetary gear carrier 5, a housing 6, a planetary gear set 7, a planetary gear set 8, a compensating gear (wide) 9, a compensating gear bolt 11, a compensating gear bolt 12, a differential cover 13, a sun gear 14, a sun gear 15, an output shaft 17, a spur gear 18, a spur gear 19, a rolling bearing 20, a rolling bearing 21, a crimping part 23, a blind hole 25, a radial hole 26, an annular space 27, a blind hole 28, a supporting device 30, a longitudinal hole 31, a radial hole 33, a concave part 34, a floating bearing 35, a running gear part 36, a bearing 37, a containing part 38, and a shoulder 39, wherein the distance between the shoulder 39 of the spur gear of the sun gear S is input.

Claims (10)

1. A transmission device for a motor vehicle, comprising a multi-stage planetary gear set (2) and a spur gear differential (3) connected via a common planetary gear carrier (4), having a first and a second planetary gear set (6, 7) which mesh in pairs with one another, wherein each planetary gear set (6, 7) comprises a sun wheel (13, 14) which is rotationally fixedly connected to an output shaft (15, 16) of the spur gear differential (3), torque which is introduced into the transmission device (1) integrated in a housing (5) via an input shaft being transmitted from the multi-stage planetary gear set (2) into the spur gear differential (3) and subsequently onto the output shaft (15, 16) for transmission to driven wheels, wherein the meshing plane of the multi-stage planetary gear set (2) radially overlaps at least one sun wheel (13, 14) of the spur gear differential (3),
It is characterized in that the method comprises the steps of,
The compensating wheel pins (10, 11) of the multi-stage planetary gear set (2) are guided at radial distances from the sun wheels (13, 14) through the engagement plane of the spur gear differential (3) and radially and axially fix the differential cover (12) on the end face, and the planet carrier (4) is supported in the housing (5) via a floating bearing (34) which is obtained by the toothed engagement of the input sun wheel (39) of the multi-stage planetary gear set (2) and the spur gear (17) forming a double planetary gear, and on the opposite side by means of the differential cover (12) via a fixed bearing (36).
2. The transmission device according to claim 1,
It is characterized in that the method comprises the steps of,
The sun gear (13) of the spur gear differential (3) is arranged at a small axial distance from the planet gear carrier (4) in the mounted state, wherein the planet gear carrier has recesses (33) in the region of the compensating gear bolts (10, 11).
3. The transmission device according to claim 1,
It is characterized in that the method comprises the steps of,
The outer envelope circle of the spur gear differential (3) is designed to be smaller than the inner diameter of the associated gear ring.
4. The transmission device according to claim 1,
It is characterized in that the method comprises the steps of,
The compensating wheel pins (10, 11) of the spur gear differential (3) are fixed in a form-fitting manner in the installed state at least axially via the component geometry of the differential cover (12) and of the planetary carrier (4).
5. The transmission device according to claim 4,
It is characterized in that the method comprises the steps of,
The planetary gear bolts (21) of the multi-stage planetary gear set (2) are fixed in position to the planetary gear carrier (4) or to the differential cover (12) at both ends by means of pressure-contact parts (22, 23).
6. The transmission device according to claim 5,
It is characterized in that the method comprises the steps of,
Spur gears (17, 18) of the multistage planetary gear set (2) are rotatably supported on the planetary gear bolts (21) via rolling bearings (19, 20).
7. The transmission device according to claim 4,
It is characterized in that the method comprises the steps of,
In order to lubricate the bearing device (29) of the compensating wheel (8, 9) of the spur gear differential (3), an oil pan (31) is inserted at the end into a longitudinal bore (30) of the compensating wheel pin (10, 11).
8. The transmission device according to claim 5,
It is characterized in that the method comprises the steps of,
In order to lubricate the rolling bearings (19, 20) of the spur gears (17, 18) of the multistage planetary gear set (2), the planetary gear bolts (21) have blind holes (24) and radial holes (25).
9. The transmission device according to claim 1,
It is characterized in that the method comprises the steps of,
In order to produce the teeth of the compensating gear (8, 9) of the spur gear differential (3) and/or the spur gears (17, 18) of the multi-stage planetary gear set (2), powerful scraping teeth are provided.
10. Transmission device according to any of the preceding claims,
It is characterized in that the method comprises the steps of,
The transmission device (1) is used in a powertrain of an E-axle coupled by the transmission device (1) to an electric motor.
CN202080055478.8A 2019-08-05 2020-07-15 Compact transmission device with multi-stage planetary gear set and spur gear differential Active CN114207321B (en)

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