EP3532748A1 - Groupe motopropulseur, en particulier groupe motopropulseur hybride pour un véhicule à moteur - Google Patents

Groupe motopropulseur, en particulier groupe motopropulseur hybride pour un véhicule à moteur

Info

Publication number
EP3532748A1
EP3532748A1 EP17784964.3A EP17784964A EP3532748A1 EP 3532748 A1 EP3532748 A1 EP 3532748A1 EP 17784964 A EP17784964 A EP 17784964A EP 3532748 A1 EP3532748 A1 EP 3532748A1
Authority
EP
European Patent Office
Prior art keywords
planetary gear
drive train
lubricant
electric machine
cooling
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP17784964.3A
Other languages
German (de)
English (en)
Inventor
Gerhard Magnussen
Björn Becker
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Volkswagen AG
Original Assignee
Volkswagen AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Volkswagen AG filed Critical Volkswagen AG
Publication of EP3532748A1 publication Critical patent/EP3532748A1/fr
Withdrawn legal-status Critical Current

Links

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
    • 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/04—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion with internally-toothed 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/46—Gearings having only two central gears, connected by orbital gears
    • F16H3/48—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears
    • F16H3/52—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears
    • F16H3/56—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears both central gears being 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
    • F16H3/724—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously using external powered electric machines
    • 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
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
    • 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
    • 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
    • F16H57/0476—Electric machines and gearing, i.e. joint lubrication or cooling or heating thereof
    • 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
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H2057/02034—Gearboxes combined or connected with electric machines

Definitions

  • Powertrain in particular hybrid powertrain for a motor vehicle
  • the invention relates to a drive train, in particular a hybrid drive train for a motor vehicle according to the features of the preamble of claim 1.
  • Motor vehicles in particular a plurality of hybrid powertrains for
  • Such a drive train has at least one
  • Electric machine in particular an electric motor.
  • a drive train is known for example from DE 10 2001 217 762 A1, where the electric machine is provided and / or arranged in the region of the output, in particular in the region of a differential.
  • Electric machine provided in the region of a differential, in particular arranged coaxially to a driven via the differential wheel drive shaft.
  • Electric machine is functionally effective with the output, namely with the drive wheel of the differential or connected to the differential case, wherein at least one planetary gear is provided for transmitting torque from the electric machine to the output, ie to the differential (or vice versa).
  • Planetary gear has a planetary gear housing and a first and second planetary gear stage with the respective components.
  • Planetary gear stage comprises a first sun gear, a plurality of first planetary gears and a first ring gear
  • the second planetary gear stage comprises a second sun gear, a plurality of second planetary gears and a second ring gear.
  • the first and second ring gear is formed as a common ring gear and arranged substantially on the inside of the planetary gear housing or here as an integral
  • first and the second ring gear as a common ring gear limits the constructive possibilities for a bearing of the components of the first and second planetary gear stages.
  • the arrangement, training and / or the number of required bearings construction and / or assembly-consuming that between the planetary gear stages and / or within a
  • Planet gear stage required game is achievable only through a complex specific storage of the components, whereby the design, installation and / or the cost is correspondingly large.
  • a cooling and / or a lubricant reservoir in particular a
  • Oil reservoir known in which over a variety of oil channels an oil supply point sufficient oil is provided, in particular independent of a change in the speed of the vehicle.
  • the invention is therefore based on the object, the generic drive train from which the invention proceeds, now such and further develop that the design and / or assembly costs is reduced, in particular a simple cooling or lubrication of the components of the respective planetary gear stage is possible.
  • the first and the second ring gear is each formed as a separate ring gear, so that the first and second ring gear is spaced from each other can be arranged.
  • a further component namely a stationary bearing plate at least partially disposed between the first and the second ring gear and / or provided or at least partially extend between the first and the second Hohrad in the direction of the interior of the planetary gear housing.
  • the bearing plate With the aid of the bearing plate provided in this way, it is at least partially possible to realize a mounting of components of the first and / or the second planetary gear stage and / or at least partially to provide coolant and / or lubricant supply to components of the first and / or the second planetary gear stage.
  • a bearing plate between the first and the second ring gear is provided which can extend in particular from the inner wall of the planetary gear housing in the direction of the interior of the planetary gear housing, on the one hand because the bearing plate "fixed", this bearing plate can be used to a structurally simple and realize cost-effective storage of specific components of the respective planetary gear stage, and / or on the other hand, this bearing plate, in particular at the same time, also used or used to realize the necessary cooling and / or lubricant supply, in particular of specific components of the first and / or second planetary gear stage
  • the construction and assembly costs for the storage of the components of the respective planetary gear stage is therefore correspondingly reduced, wherein in particular at the same time a corresponding cooling and / or lubricant supply to the components of the first and / or the second planetary gear stage is ensured in a simple manner, and now - in particular, as a whole - a simple storage and cooling or lubricant supply concept can be realized.
  • Lubricant reservoir outside of the planetary gear housing are led into the interior of the planetary gear housing, in particular to specific locations.
  • the electric machine is arranged coaxially to a wheel drive shaft, wherein the first and second planetary gear stage are arranged substantially sequentially one behind the other.
  • the drive shaft of the electric machine in particular a rotor shaft is rotatably connected to the first planetary gear stage, wherein the first planetary gear stage rotationally effective with the second planetary gear stage and the second planetary gear stage rotatably connected via the output, in particular via the differential to the wheel drive shaft and / or connectable.
  • Radantriebswelle allows, in particular when the electric machine is used as an electric motor, or (conversely) a generator operation of
  • Electric machine as electric motor or as a generator is therefore feasible accordingly.
  • Planet wheel with the second sun gear rotatably coupled, in particular rotationally fixed, wherein a planet carrier of the second planetary gear with the output, in particular with the drive wheel of the differential and / or the differential housing is coupled in a rotationally effective manner.
  • the planet carrier of the second planetary gear of the second planetary gear stage is designed as an "interface", so that the already known in the prior art gear / differentials with the respective electric machine and the planetary gear can also be retrofitted.
  • the bearing plate is now substantially annular and extends substantially inwardly starting from the planetary gear housing, in particular from the inner wall of the planetary gear housing.
  • the bearing plate On the inner circumference of the bearing plate is a first bearing receiving area and in the central region of the bearing plate, a second bearing receiving area for the arrangement of corresponding bearing elements, which will be explained in more detail below, is provided. Due to the appropriate design of the bearing plate are on the one hand
  • a first bearing element is arranged on the first bearing receiving area of the bearing plate, which at least partially for the Storage of the first planet carrier and / or is provided for the storage of the second sun gear.
  • the first bearing element is a
  • Deep groove ball bearings designed to absorb radial and axial forces. As a result, the second sun gear can be stored essentially without any significant play.
  • a second bearing element can be arranged, which is provided for the at least partial mounting of the second planet gear carrier.
  • the second bearing element is as an axial needle bearing for receiving axial forces and / or to enable a radial clearance of the second
  • Planetary gear housing in particular in each case is arranged rotationally fixed, on the one hand, a corresponding balance between the first and second planetary gear stage, on the other hand enables a radial clearance of the second planetary gear stage.
  • the second ring gear is arranged substantially without an effective radial clearance, so the game of "interface” is essentially determined by the "specific component of the storage of the second planet carrier” and / or on the game of the second bearing element, in particular a minimum how a maximum clearance of the second planet carrier is set in the radial direction or previously determined.
  • the second bearing element is as a
  • the drive shaft of the electric machine in particular the rotor shaft as a
  • Electric motor running electric machine is mounted with the help of a third bearing element, in particular by means of a deep groove ball bearing in the radial direction substantially free of play.
  • the first sun gear of the first planetary gear stage is in particular formed as an integral part of the drive shaft, in particular of the rotor shaft of the electric machine.
  • the second planet carrier has an extension, which is designed as an interface that can be connected in terms of rotation with the output, wherein the end region of the extension is designed to be partially scored in particular on the inner circumference. This allows the corresponding end region of the extension, in particular due to the Sliding easily on a geritztelt on the outer circumference drive wheel of the differential or connect to an output according to previously described realized game.
  • a cooling and / or lubricant reservoir is provided, in particular is attached directly to the planetary gear housing.
  • the coolant and / or lubricant reservoir is fluidly connected to the interior of the planetary gear housing at least over the end shield.
  • the bearing plate has at least one formed flow channel which communicates with the coolant and / or lubricant reservoir
  • Planetary gear stage easily coolable and / or lubricated.
  • the filling of the flow channel of the bearing plate is using the in the cooling and / or
  • Lubricant reservoir existing hydrostatic pressure, in particular without a separate pumping device possible.
  • Lubricant reservoir provided at least partially vertically arranged and / or at least partially vertically extending feed pipe (overflow pipe) or the flow channel of the bearing plate to the feed pipe in particular via a corresponding further feed channel fluidly connected.
  • This flow connection is structurally simple to design and inexpensive to produce.
  • the bearing plate and / or the flow channel of the bearing plate has at least one cooling and / or lubricant outlet opening.
  • the flow channel has a plurality of cooling and / or lubricant outlet openings, with the aid of which the coolant and / or lubricant can be fed to the specific components of the first and / or second planetary gear stage locally or to these specific locations, this may be explained in more detail below ,
  • At least one guide element in particular a guide plate for guiding and / or discharging at least one part of the coolant and / or lubricant, in particular to the fourth, is located substantially adjacent to the first and / or second planet carrier of the first and / or second planetary gear
  • Bearing elements which are arranged for mounting the planetary gears provided.
  • the middle region of the interior of the gears In particular, in the middle region of the interior of the gears
  • Planetary gear housing provided specific components, in particular the first and second planet carrier or provided here in particular for supporting the planetary gears or trained webs and provided for the storage of the planetary gears, in particular fourth bearing elements can cool and / or lubricate using the bearing plate in a simple manner ,
  • the planetary gear housing has a cooling and / or
  • Lubricant planer for realizing a return of the cooling and / or
  • Lubricant from the interior of the planetary gear housing back into the coolant and / or lubricant reservoir corresponding further flow channels and / or outlet openings for realizing the return of the coolant and / or lubricant from the interior of the planetary gear housing are provided in the coolant and / or lubricant reservoir.
  • a corresponding coolant and / or lubricant circuit with a corresponding drive of the planetary gear preferably due to the then acting on the coolant and / or lubricant centrifugal forces, caused by the
  • Drivetrain designed as a hybrid powertrain for a motor vehicle and especially in a four-wheel drive vehicle to drive the front axle
  • Fig. 1 in a simplified schematic representation of essential components of the drive train according to the invention partly in section, but only in a so-called “half-tone representation", in particular for clarity of the bearing concept realized here for the storage of the components of the first and second planetary gear stage,
  • FIG. 2 is a simplified schematic representation substantially analogous to Figure 1, the essential components of the drive train according to the invention, in particular arranged in the planetary gear housing components of the first and second planetary gear stage including the partial representation of guide elements for implementing a cooling and / or lubricant supply.
  • Fig. 3 in a schematically partially sectioned view of the side of the
  • Planetary gear and an affiliated to the planetary gear housing cooling and / or lubricant reservoir including a simplified representation of the realized cooling and / or lubricant supply
  • Fig. 4 shows the first and second planetary gear set including a simplified schematically illustrated coolant or lubricant flow.
  • FIG. 1 to 4 show at least partially in each case in a simplified schematic representation, in particular Figs. 1 and 2 in a so-called "half
  • the electric machine 2 and / or the planetary gear 3 are provided in the region of an output, in particular in the region of an output 4, in particular in the region of a differential 4a, wherein the output 4 or the differential 4a is not shown in detail, but should only be symbolized by the arrow shown in FIGS. 1 and 2.
  • the electric machine 2 is operatively connected to the output 4, in particular with a drive wheel of the differential 4a and / or connected to a differential housing or connectable.
  • the planetary gear 3 has a planetary gear housing 3a and a first and second planetary gear stage I and II.
  • the first planetary gear stage I or the second planetary gear stage II has respective corresponding specific components.
  • the first planetary gear stage I has at least one first sun gear 5, at least one first planet gear 6 and at least one first ring gear 7.
  • the first planetary gear stage I is designed as a so-called "input stage”.
  • the second planetary gear stage II has at least one second sun gear 8, at least one second planet gear 9 and at least one second ring gear 10.
  • the second planetary gear stage II is designed as a so-called "load stage”.
  • first planetary gear stage I or the second planetary gear stage II has a plurality of first and second planetary gears 6 and 9, respectively, in each case between three and five first
  • the at least partially shown in FIGS. 1 to 4 drive train 1, in particular the hybrid powertrain 1 a is provided for a motor vehicle and in particular in the range of a not shown in detail here output 4, in particular in the range of a differential 4a can be arranged, wherein for the transmission of Torques between the electric machine 2 and the output 4 and the differential 4a, the planetary gear 3 is provided with the first and second planetary gear I and II or arranged accordingly.
  • the drive train 1, here is a hybrid powertrain 1 a for a motor vehicle with
  • first ring gear 7 and the second ring gear 10 are each formed as a separate ring gear 7 and 10, wherein the first and the second ring gear 7 and 10th so spaced apart and / or provided so that a fixed bearing plate 1 1 at least partially between the first and the second ring gear 7 and 10 in the direction of the interior of the 3b
  • Planetary gear housing 3a arranged extending and / or is provided, and wherein with the aid of the bearing plate 1 1 at least partially a storage of
  • the electric machine 2 is arranged coaxially to a wheel drive shaft 12.
  • the wheel drive shaft 12 is essentially driven in accordance with the output 4, in particular via the differential 4a.
  • Planetary gear I and II arranged substantially sequentially one behind the other.
  • the drive shaft 2 a of the electric machine 2 is rotatably connected to the first planetary gear stage I, wherein the first planetary gear stage I rotationally effective with the second planetary gear stage II and the second
  • Planetary gear stage II rotationally effective on the output 4 not shown here in detail, in particular via the differential 4a not shown here in detail connected to the wheel drive shaft 12 and / or connectable.
  • the electric machine 2 is designed here as an electric motor or the drive shaft 2 a as a rotor shaft.
  • Fig. 1 shows the electric machine 2 with the drive shaft 2a and the rotor shaft, wherein in the embodiment shown here at the end of the drive shaft 2a, the first sun gear 5 in
  • Planetary gear I is therefore in particular an integral part of
  • Drive shaft 2a formed.
  • a sun gear arranged separately on the drive shaft and / or a subdivision of the drive shaft into a plurality of sections / segments and / or corresponding connections to the electric machine, in particular to the rotor and / or a rotor carrier of the electric machine.
  • FIGS. 1 and 2 can be seen a first Planetenradtrager 13 of the first planetary gear 6 and a second Planetenradtrager 14 of the second
  • the first Planetenradtrager 13 serves to support the first planetary gear 6 and has for this purpose in particular a web 13a
  • the second Planetenradtrager 14 serves to support the second planetary gear 9 and has for this purpose in particular a web 14a.
  • the first Planetenradtrager 13 is rotationally effective with the second sun gear 8, in particular rotatably coupled, wherein the second
  • Planetenradtrager 14 with the output 4 rotationally effective, in particular rotatably coupled.
  • the bearing plate 1 1 is substantially annular and extends substantially inwardly, starting from an unspecified inner wall of the planetary gear housing 3a radially inwardly, in particular in the direction of
  • Planetary gear housing 3a arranged or supported accordingly.
  • Inner circumference of the bearing plate 1 1 is a first bearing receiving portion 1 1 b and in the central region of the bearing plate 1 1, a second bearing receiving portion 1 1 c provided.
  • the bearing receiving areas 1 1 b and 1 1 c serve to accommodate and / or arrangement of corresponding bearing elements, which will be explained in more detail below.
  • the first and second bearing receiving area 1 1 b and 1 1 c by substantially on the inner periphery of the bearing plate 1 first mitigateorkragende areas or limited by unspecified projections in particular at least one side.
  • a first bearing element 15 is arranged, which is at least partially provided for the storage of the first Planetenradtragers 13 and / or for the storage of the second sun gear 8.
  • the first bearing element 15 is designed here in particular as a deep groove ball bearing for receiving radial and axial forces.
  • Bearing element 16 is arranged.
  • the second bearing element 16 serves to at least partially support the second planet carrier 14, wherein the second
  • Bearing member 16 is designed in particular as an axial needle bearing for receiving axial forces and / or to enable radial play of the second planet carrier 14.
  • FIG. 1 and 2 show that here two second bearing elements 16 are provided for mounting the second planet carrier 14, wherein a second bearing element 16 on the second bearing receiving portion 1 1 c of the bearing plate 1 1 is arranged and the other second bearing element 16 substantially on the other side of the second planet carrier 14 between the second planet carrier 14 and a
  • Inner wall of the planetary gear housing 3a is arranged or provided.
  • the first ring gear 7 of the first planetary gear stage I is arranged with an effective radial clearance, in particular in a not designated here recess of the planetary gear housing 3a.
  • Planetary gear stage II is arranged substantially without effective radial play on the planetary gear housing 3a.
  • the second ring gear 10 may in particular also be formed as an integral part of the planetary gear housing 3a.
  • the first and second ring gear 7 and 10 each rotatably on
  • Planetary gear housing 3a arranged.
  • FIGS. 1 and 2 show that the drive shaft 2 a of the electric machine 2 is mounted essentially free of play in the radial direction with the aid of a third bearing element 17, in particular with the aid of a deep groove ball bearing.
  • the third bearing element 17 also serves to support the first sun gear 5, which is in particular formed as an integral part of the drive shaft 2a, in particular a rotor shaft.
  • the first planet carrier 13 is mounted with two first bearing elements 15, wherein a first bearing element 15 on the inner circumference of the bearing plate 1 1, namely in the first bearing receiving portion 1 1 b is arranged and the second first bearing element 15 substantially on the other side of the
  • Planetenradtragers 13 is provided between an unspecified housing wall of the electric machine 2 and a corresponding extension of the first planet carrier 13.
  • FIGS. 1 and 2 show that the second planet carrier 14 has an extension 14a, which is designed as an interface that can be connected to the output 4 in a rotationally effective manner.
  • the end portion of the extension 14b is formed on the inner circumference in particular geritzel, so that in this way an "interface" is formed, so that the unit shown in Fig. 1 and 2 of the electric machine 2 and planetary gear 3 substantially to a not-shown here driving a Downforce 4 and / or to a substantially thereby formed
  • Differential housing 4a can be pushed.
  • the first planet carrier 13 is guided very precisely, in particular in the radial direction, wherein the second planet carrier 14 in the radial direction has a certain, in particular certain game, so that here by the second
  • Planet wheel 14 in particular by the extension 14b formed "interface" easily mounted, in particular on the drive wheel of an output 4, in particular a differential 4a can be pushed.
  • Nonuniformity is ensured in the second planetary gear stage II, in particular in the load stage, wherein the second ring gear 10 is positioned substantially free of play on the planetary gear housing 3a. Since the second sun gear 8 on the The first planetary gear carrier 13 is positioned substantially play-free, the radial clearance of the second planetary gear carrier 14 is determined substantially by the second bearing elements 16.
  • the planetary gears, here the first and second planetary gears 6 and 9 are rotatably supported via fourth bearing elements 18 on the respective webs 13a and 14a of the planet carrier 13 and 14, respectively.
  • the bearing plate 1 1 is designed as a separate component and arranged with the aid of the support portion 1 1 a on the unspecified inner wall of the planetary gear housing 3a.
  • a locking ring is provided. It is also conceivable that the bearing plate is formed as an integral part of the planetary gear housing or on a
  • Ring gear in particular arranged on the second ring gear, in particular
  • bearing plate 1 1 is welded.
  • the formation of the bearing plate 1 1 as a separate component has proven to be particularly advantageous and inexpensive.
  • FIGS. 2 to 4 are identical to FIGS. 2 to 4:
  • Fig. 3 shows that outside the planetary gear housing 3a, a cooling and / or lubricant reservoir 19 is provided outside the planetary gear housing 3a.
  • Lubricant reservoir 19 is connected to the interior 3b of the planetary gear housing 3a fluidly connected at least over the end plate 1 1. This can be seen in particular partially from FIG. 3 and also from FIG. 4.
  • the bearing plate 1 1 has at least one flow channel 1 1 d and / or limited, in particular on the inner circumference also a partially annular
  • Flow channel 1 1 e runs essentially from
  • Flow channel 1 1 e is partially annular on the inner circumference of the bearing plate 1 1.
  • the flow channels 1 1 d and 1 1 e are each other
  • the feed tube 20 can also be referred to as an "overflow tube", wherein the feed channel 21 is in particular also at least partially formed in the planetary gear housing 3a, as can be seen from FIG.
  • the bearing plate 1 1 and / or the flow channel 1 1 d or 1 l e has at least one cooling and / or lubricant outlet opening 1 1f, or even more lubricant outlet openings 1 1 f.
  • the bearing plate 1 1 and / or the flow channel 1 1 d or 1 l e has at least one cooling and / or lubricant outlet opening 1 1f, or even more lubricant outlet openings 1 1 f.
  • Lubricant outlet opening 1 1 f formed at the radial inner end of the flow channel 1 1 d.
  • the flow circuit of the coolant and / or lubricant is
  • first and / or second planet carrier 13 or 14 of the first and / or second planetary gear 6 or 9, in particular in the region of the webs 13a and 14a at least one guide element 22, in particular a baffle 22a for guiding and / or discharging at least part of the cooling and / or Lubricant is provided in particular to the fourth bearing elements 18 of the first and second planet gears 6 and 9, respectively.
  • the first planet 13 have a radially outwardly projecting, unspecified here extension, which fulfills the function of an oil collector in a certain area of the planetary gear housing 3a.
  • a guide element 22 is arranged or provided in the region of the web 13a.
  • the planetary gear housing 3a has a coolant and / or lubricant planer 23 for realizing a return of the coolant and / or lubricant from the interior 3b of the planetary gear housing 3a back into the coolant and / or lubricant reservoir 19 and / or according to further flow channels, in particular an outlet opening 24 here.
  • the flow of coolant and / or lubricant is represented or symbolized by the corresponding arrows in FIGS.
  • the first and second planet gears 6 being in operation of the drive train 1, in this case of the hybrid drive train 1 a, in particular due to the direction of rotation (when the motor vehicle moves forwards) or 9 with the aid of the cooling and / or lubricant planer 23, the thrown to the inner wall of the planetary gear housing 3a coolant and / or lubricant
  • the cooling and / or lubricant concept is realized without a pump, but the arrangement of an additional, in particular electrically operated, pump is also conceivable. Because the coolant and / or lubricant is collected in a coolant and / or lubricant reservoir 19 outside the planetary gear 3, splash losses in the planetary gear 3 are avoided. These measures lead to a high efficiency of the planetary gear 3 and minimize the costs associated with the cooling and / or lubricant concept.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Details Of Gearings (AREA)
  • Retarders (AREA)

Abstract

L'invention concerne un groupe motopropulseur (1), en particulier un groupe motopropulseur hybride (1a) pour un véhicule à moteur, comprenant au moins un moteur électrique (2), ce dernier (2) étant disposé dans la zone d'une sortie (4), en particulier dans la zone d'un différentiel (4a), le moteur électrique (2) étant raccordé et/ou pouvant être raccordé de manière fonctionnelle à la sortie (4), en particulier à un pignon d'entraînement du différentiel (4a) et/ou au carter de différentiel, ledit groupe motopropulseur comprenant au moins une boîte de vitesses à trains épicycloïdaux (3) servant à transmettre des couples de rotation du moteur électrique (2) à la sortie (4) (ou inversement), la boîte de vitesses à trains épicycloïdaux (3) présentant un carter (3a) et un premier et un deuxième étage (I, II) comportant des composants respectifs, à savoir le premier étage (I) comprenant au moins un premier pignon planétaire (5), au moins un premier satellite (6) et au moins une première couronne (7) et/ou le deuxième étage (II) présentant au moins un deuxième pignon planétaire (8), au moins un deuxième satellite (9) et au moins une deuxième couronne (10). La complexité de conception et de montage est réduite par le fait que la première couronne (7) et la deuxième couronne (10) sont réalisées chacune sous la forme d'une couronne séparée (7, 10), la première et la deuxième couronne (7, 10) étant espacées l'une de l'autre de sorte qu'un flasque fixe (11) s'étend au moins en partie entre la première et la deuxième couronne (7, 10) en direction du compartiment intérieur (3b) du carter (3a), et une alimentation en fluide de refroidissement et/ou en lubrifiant de composants du premier et/ou du deuxième étage (I, II) étant réalisée au moins en partie à l'aide du flasque (11).
EP17784964.3A 2016-10-25 2017-10-18 Groupe motopropulseur, en particulier groupe motopropulseur hybride pour un véhicule à moteur Withdrawn EP3532748A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016220951.5A DE102016220951A1 (de) 2016-10-25 2016-10-25 Antriebsstrang, insbesondere Hybridantriebsstrang für ein Kraftfahrzeug
PCT/EP2017/076576 WO2018077688A1 (fr) 2016-10-25 2017-10-18 Groupe motopropulseur, en particulier groupe motopropulseur hybride pour un véhicule à moteur

Publications (1)

Publication Number Publication Date
EP3532748A1 true EP3532748A1 (fr) 2019-09-04

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Application Number Title Priority Date Filing Date
EP17784964.3A Withdrawn EP3532748A1 (fr) 2016-10-25 2017-10-18 Groupe motopropulseur, en particulier groupe motopropulseur hybride pour un véhicule à moteur

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Country Link
EP (1) EP3532748A1 (fr)
CN (1) CN109844366A (fr)
DE (1) DE102016220951A1 (fr)
WO (1) WO2018077688A1 (fr)

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WO2022201538A1 (fr) * 2021-03-26 2022-09-29 武蔵精密工業株式会社 Dispositif de transmission de puissance

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2962071B2 (ja) * 1992-09-11 1999-10-12 トヨタ自動車株式会社 電気自動車用駆動装置
JP4039351B2 (ja) 2003-10-16 2008-01-30 トヨタ自動車株式会社 車両用のオイル供給装置
DE102009031320B4 (de) * 2009-06-30 2016-10-06 Siemens Aktiengesellschaft Planetengetriebe
DE102009034833A1 (de) * 2009-07-27 2011-02-03 Siemens Aktiengesellschaft Planetengetriebe
DE102010036884B4 (de) * 2010-08-06 2023-08-10 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Antriebssystem und Kraftfahrzeug mit einem derartigen Antriebssystem
ES2472698T3 (es) * 2011-11-17 2014-07-02 Siemens Aktiengesellschaft Engranaje para una instalación de energía e�lica
CN103195877A (zh) * 2013-04-18 2013-07-10 南京高精齿轮集团有限公司 用于球磨机的多级行星减速机
DE102014217762A1 (de) * 2014-09-05 2016-03-10 Volkswagen Aktiengesellschaft Hybridantriebsstrang für ein Kraftfahrzeug
WO2016116042A1 (fr) * 2015-01-20 2016-07-28 北京华擎变速器工程技术研究院 Boite de vitesses cylindrique
DE102015203068A1 (de) 2015-02-20 2016-09-08 Volkswagen Aktiengesellschaft Hybridantriebsstrang für ein Kraftfahrzeug

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CN109844366A (zh) 2019-06-04
WO2018077688A1 (fr) 2018-05-03
DE102016220951A1 (de) 2018-04-26

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