WO2017138312A1 - 車両駆動装置 - Google Patents

車両駆動装置 Download PDF

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Publication number
WO2017138312A1
WO2017138312A1 PCT/JP2017/001453 JP2017001453W WO2017138312A1 WO 2017138312 A1 WO2017138312 A1 WO 2017138312A1 JP 2017001453 W JP2017001453 W JP 2017001453W WO 2017138312 A1 WO2017138312 A1 WO 2017138312A1
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WO
WIPO (PCT)
Prior art keywords
gear
notch
casing
lubricating oil
drive device
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Application number
PCT/JP2017/001453
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English (en)
French (fr)
Japanese (ja)
Inventor
友明 兼子
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Ntn株式会社
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Filing date
Publication date
Application filed by Ntn株式会社 filed Critical Ntn株式会社
Publication of WO2017138312A1 publication Critical patent/WO2017138312A1/ja

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    • 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

Definitions

  • the present invention relates to a vehicle drive device including an electric motor and a speed reducer that decelerates the power of the electric motor and transmits it to drive wheels.
  • Patent Document 1 discloses a vehicle drive device that includes two electric motors and a speed reducer that independently drive left and right drive wheels.
  • this type of vehicle drive device includes an electric motor for driving independently for each of the left and right drive wheels, a single motor drive device that drives the left and right drive wheels with a single common electric motor is provided. This has the advantage that a differential gear or the like that distributes the driving force of the two electric motors to the left and right is unnecessary.
  • a conventional vehicle drive device including two conventional electric motors and a speed reducer disclosed in Patent Document 1 and left and right electric motors 101L and 101R for individually driving left and right drive wheels and electric Reducers 102L and 102R that decelerate the rotation of the motors 101L and 101R are provided, and the reducers 102L and 102R are arranged at the center of the left and right electric motors 101L and 101R.
  • the reduction gears 102 ⁇ / b> L and 102 ⁇ / b> R are driven wheels via an input gear shaft 123 having an input gear to which power is transmitted from the motor shaft 112, and a drive shaft including a constant velocity joint 126 and an intermediate shaft 127. And an output gear shaft 125 that transmits a driving force to the input gear shaft 123, and the input gear shaft 123 and the output gear shaft 125 are arranged in parallel and offset from each other.
  • One or more intermediate gear shafts 124 are provided between the input gear shaft 123 and the output gear shaft 125 of the speed reducers 102L and 102R.
  • the left and right speed reducers 102L and 102R are accommodated in parallel in a single speed reducer casing 128.
  • a predetermined amount of lubricating oil is sealed in order to lubricate the gear trains constituting the left and right reduction gears 102L, 102R. Then, the lubricating oil is splashed by the operation of the gears, and oil splashes generated at that time are supplied to the tooth surfaces of the gears of the reduction gear and the rolling bearings.
  • the reducer casing is provided with a plurality of thinnings on the inner wall surface for the purpose of weight reduction, and the wall thickness is provided between the thinnings for ensuring rigidity.
  • the lubricating oil splashed on the inner wall surface of the reducer casing flows down along the wall surface.
  • the lubricating oil accumulates in the thin wall of the inner wall surface, and the lubricating oil cannot be effectively used. .
  • an object of the present invention is to provide a vehicle drive device that can efficiently supply lubricating oil accumulated on the inner wall surface of the reduction gear casing to the rolling bearing.
  • the present invention includes an electric motor and a speed reducer that decelerates the power of the electric motor and transmits the power to the drive wheels.
  • the speed reducer is an input to which power is transmitted from the motor shaft.
  • An input gear shaft having gears, an output gear shaft having an output gear for transmitting a driving force to the drive wheels, and one or more intermediate gear shafts having an intermediate gear provided between the input gear shaft and the output gear shaft;
  • the respective gear shafts are supported via rolling bearings fitted in bearing fitting holes provided in the casing.
  • a plurality of partition walls are formed by a fillet provided on the inner wall surface of the casing, and a notch is provided on the bearing fitting hole side of at least one partition wall located above the bearing fitting hole.
  • the meat The lubricating oil accumulated in body, characterized in that it discharged to the rolling bearing side.
  • a communication groove that communicates the space for housing the reduction gear and the internal space of the bearing fitting hole is provided, and lubricating oil discharged from a notch provided in the partition is supplied through the communication groove. It may be configured to do so.
  • the notch and the communication groove may be provided at a position that does not intersect the line of load acting on the rolling bearing due to meshing of the gears.
  • the notch may be provided in the partition located above the communication groove.
  • the lower part of the meat fillet in a tapered shape so that the lubricating oil does not remain in the meat fillet on the inner wall surface of the speed reducer casing.
  • a plurality of partition walls are formed by the fillet provided on the inner wall surface of the reduction gear casing, and the bearing fitting holes of at least one partition wall located above the bearing fitting holes are provided.
  • FIG. 1 is a cross-sectional plan view showing an embodiment of a vehicle drive device to which the present invention is applied.
  • FIG. 2 is an enlarged cross-sectional plan view of the speed reducer portion of FIG. 1.
  • 1 is a schematic plan view showing an example of an electric vehicle using a vehicle drive device according to the present invention. It is a top view of embodiment of FIG. It is explanatory drawing made into the cross section by the VV line of FIG. It is explanatory drawing which looked at the gear train of embodiment of FIG. 1 from the axial direction.
  • FIG. 6 is an explanatory view taken along a line VII-VII in FIG. 5.
  • FIG. 8 is an enlarged view of a region VIII portion surrounded by a broken line in FIG.
  • FIG. 4 is an enlarged view of a region IV portion surrounded by a broken line in FIG. 1. It is a cross-sectional top view which shows the conventional 2 motor type vehicle drive device.
  • the two-motor type vehicle drive device A shown in FIG. 1 has a reduction gear casing 20 that houses two reduction gears 2L and 2R in parallel in the left and right directions, and two electric motors 1L on the left and right sides of the reduction gear casing 20.
  • 1R motor casings 3L and 3R are fixedly arranged.
  • An electric vehicle C shown in FIG. 3 is a front-wheel drive system, and is a two-motor vehicle drive device that independently drives a chassis 51, front wheels 52 as drive wheels, rear wheels 53, and left and right drive wheels.
  • a two-motor type vehicle drive device A is mounted on a chassis 51 at the center of left and right front wheels 52 as drive wheels, and the driving force of the two-motor type vehicle drive device A is a constant velocity joint. 15 and the intermediate shaft 16 are transmitted to the front wheels 52 which are left and right drive wheels.
  • a rear wheel drive system or a four wheel drive system may be used in addition to the front wheel drive system shown in FIG.
  • the left and right electric motors 1L, 1R in the two-motor vehicle drive device A are accommodated in motor casings 3L, 3R as shown in FIG.
  • the motor casings 3L and 3R include cylindrical motor casing bodies 3aL and 3aR, outer walls 3bL and 3bR that close the outer surfaces of the motor casing bodies 3aL and 3aR, and reduction gears on the inner surfaces of the motor casing bodies 3aL and 3aR. It consists of inner walls 3cL and 3cR separated from 2L and 2R. The inner walls 3cL and 3cR of the motor casing bodies 3aL and 3aR are provided with openings for drawing out the motor shaft 12a.
  • the electric motors 1 ⁇ / b> L and 1 ⁇ / b> R are of a radial gap type in which a stator 11 is provided on the inner peripheral surface of the motor casing body 3 aL and 3 aR, and a rotor 12 is provided on the inner periphery of the stator 11. I am using something.
  • the electric motors 1L and 1R may be axial gap types.
  • the rotor 12 has a motor shaft 12a at the center, and the motor shaft 12a is drawn from the openings of the inner side walls 3cL and 3cR of the motor casing bodies 3aL and 3aR to the speed reducers 2L and 2R, respectively.
  • a seal member 13 is provided between the openings of the motor casing bodies 3aL and 3aR and the motor shaft 12a.
  • the motor shaft 12a is rotatably supported by the rolling bearings 14a and 14b on the inner side walls 3cL and 3cR and the outer side walls 3bL and 3bR of the motor casing main bodies 3aL and 3aR (FIG. 1).
  • the speed reducer casing 20 that accommodates the two speed reducers 2 ⁇ / b> L and 2 ⁇ / b> R provided in parallel on the left and right is a central casing 20 a and left and right fixed to both side surfaces of the central casing 20 a. It has a three-piece structure of side casings 20bL and 20bR. The left and right side casings 20bL and 20bR are fixed to the openings on both sides of the central casing 20a by a plurality of bolts 26L and 26R.
  • the side surfaces of the side casings 20bL and 20bR of the reduction gear casing 20 on the outboard side (outside of the vehicle body) and the motor casing bodies 3aL and 3aR of the electric motors 1L and 1R are fixed to the inner side walls 3cL and 3cR by a plurality of bolts 29.
  • the two electric motors 1L and 1R are fixedly arranged on the left and right sides of the reduction gear casing 20 (FIGS. 1 and 4).
  • a partition wall 21 is provided in the center of the center casing 20a.
  • the reduction gear casing 20 is divided into two left and right by the partition wall 21, and independent left and right accommodation chambers for accommodating the two reduction gears 2L and 2R are provided in parallel.
  • the speed reducers 2L and 2R are provided symmetrically and have large input gear shafts 23L and 23R each having an input gear 23a to which power is transmitted from the motor shaft 12a, and the input gear 23a.
  • the intermediate gear shafts 24L and 24R having small diameter gears 24b meshing with the diameter gear 24a and the output gear 25a, and the output gear 25a are pulled out from the speed reducer casing 20, and the constant velocity joint 15 and the intermediate shaft 16 (FIG. 3) are connected.
  • It is a parallel shaft gear reducer provided with the output gear shafts 25L and 25R that transmit the driving force to the drive wheels via the shafts.
  • the input gear shafts 23L and 23R, the intermediate gear shafts 24L and 24R, and the output gear shafts 25L and 25R of the two left and right speed reducers 2L and 2R are coaxially arranged.
  • Both ends of the input gear shafts 23L, 23R of the speed reducers 2L, 2R roll into bearing fitting holes 27a formed on both the left and right sides of the partition wall 21 of the central casing 20a and bearing fitting holes 27b formed in the side casings 20bL, 20bR.
  • the bearings 28a and 28b are rotatably supported.
  • the bottoms of the bearing fitting holes 27a and 27b are stepped and are formed with a thinner thickness on the inner peripheral side than the wall part with which the outer rings of the rolling bearings 28a and 28b abut.
  • the end portions on the outboard side of the input gear shafts 23L and 23R are drawn outward from the opening portions 27c provided in the side casings 20bL and 20bR, and the openings 27c and the outer end portions of the input gear shafts 23L and 23R are connected to each other.
  • An oil seal 31 is provided between them to prevent leakage of lubricating oil sealed in the speed reducers 2L and 2R and intrusion of muddy water from the outside.
  • the motor shaft 12a has a hollow structure, and the input gear shafts 23L and 23R are inserted into the hollow motor shaft 12a.
  • the input gear shafts 23L and 23R and the motor shaft 12a are coupled to each other by a spline (including the serrations).
  • Intermediate gear shafts 24L and 24R are stepped gear shafts having a large-diameter gear 24a meshing with the input gear 23a and a small-diameter gear 24b meshing with the output gear 25a on the outer peripheral surface.
  • rolling bearings 34a and 34b are formed into bearing fitting holes 32a formed on both surfaces of the partition wall 21 of the central casing 20a and bearing fitting holes 32b formed on the side casings 20bL and 20bR. Is supported through.
  • the bottom part of the bearing fitting holes 32a and 32b is formed in a stepped shape with a thinner thickness on the inner peripheral side than the wall part with which the outer ring of the rolling bearings 34a and 34b abuts.
  • the output gear shafts 25L and 25R have a large-diameter output gear 25a, and are formed in bearing fitting holes 35a formed on both surfaces of the partition wall 21 of the central casing 20a and bearing fitting holes 35b formed on the side casings 20bL and 20bR. It is supported by rolling bearings 37a and 37b. And the bottom part of the bearing fitting holes 35a and 35b is formed in a stepped shape in which the inner peripheral side is thinner than the wall part with which the outer ring of the rolling bearings 37a and 37b abuts.
  • Outboard side ends of the output gear shafts 25L and 25R are pulled out to the outside of the reduction gear casing 20 through openings 35c formed in the side casings 20bL and 20bR, and the output gear shafts 25L and 25R are pulled out to the outboard side.
  • the outer joint portion 15a of the constant velocity joint 15 is splined to the outer peripheral surface of the end portion.
  • the constant velocity joint 15 coupled to the output gear shafts 25L and 25R is connected to the drive wheel 52 via the intermediate shaft 16 (FIG. 3).
  • An oil seal 39 is provided between the end of the output gear shafts 25L and 25R on the outboard side and the opening 35c formed in the side casings 20bL and 20bR, and leakage of the lubricating oil sealed in the speed reducers 2L and 2R It also prevents the entry of muddy water from the outside.
  • FIG. 9 shows the intermediate gear shaft 24L
  • rolling bearings 28a and 28b are provided at both ends of the input gear shafts 23L and 23R, the intermediate gear shaft 24R, and the output gear shafts 25L and 25R, including the intermediate gear shaft 24L.
  • 34a, 34b, 37a, 37b are fitted, and the outer ring 41 of the rolling bearings 28a, 28b, 34a, 34b, 37a, 37b is fitted to the bearing fitting holes 27a, 32a, 35a of the central casing 20a and the side surfaces. It is fitted in the bearing fitting holes 27b, 32b, 35b of the casings 20bL, 20bR.
  • the inner rings 40 of the rolling bearings 28a, 28b, 34a, 34b, 37a, 37b and the gear shafts 23L, 23R, 24L, 24R, 25L, 25R are fitted with tightness so that they can be rotated at the center of rotation (tight).
  • the outer ring 41 of the rolling bearings 28a, 28b, 34a, 34b, 37a, and 37b and the bearing fitting holes 27a, 32a, 35a27b, 32b, and 35b can be easily assembled into each gear shaft.
  • the lubricating oil is positively supplied between the bearing fitting holes 27a, 32a, 35a, 27b, 32b, and 35b and the outer ring 41 of the rolling bearing.
  • the lubricating oil staying in the lower portion of the speed reducer casing 20 is splashed by the gears, and the oil droplets generated at that time are supplied to the tooth surface and the rolling bearing.
  • the lubricating oil into the bearing it is effective to generate an oil flow penetrating in the axial direction inside the bearing.
  • FIG. 9 in which the portion surrounded by the broken line IV in FIG. 1 is enlarged, the space G1 in the casing 20 housing the speed reducer and the bearing are formed on the inner peripheral surface of the bearing fitting hole 32b into which the rolling bearing 34b is fitted. At least one groove 45 communicating with the internal space G2 of the fitting hole 32b is provided. That is, as shown in FIG. 9, a space closed by a gear space G1 of the casing 20 where gears and the like exist with the rolling bearing 34b as a boundary and a bearing fitting hole 32b provided in the side casing 20bL of the casing 20 is defined as an internal space.
  • one or more communication grooves 45 for communicating the gear space G1 and the internal space G2 are provided on the inner peripheral surface of the bearing fitting hole 32b provided in the side casing 20bL to which the outer ring 41 of the rolling bearing 34b is fitted. Yes.
  • the oil flowing in from the communication groove 45 flows through the internal space G2 and is discharged through the internal space of the rolling bearing 34b, or the oil flowing in from the rolling bearing 34b passes through the internal space G2.
  • a flow discharged through the communication groove 45 is generated.
  • the lubricating oil flowing in from the communication groove 45 is positively supplied between the bearing fitting hole 32b and the outer ring 41 of the rolling bearing 34b.
  • the inner ring 40, the outer ring 41, the rolling element 42, and the communication groove 45 which are components of the rolling bearings 28a, 28b, 34a, 34b, 37a, and 37b, have the same reference numerals.
  • the speed reducer casing 20 is provided with a plurality of thinnings 20e to reduce the weight to reduce the weight, and a partition 20c is provided between the thinnings 20e to ensure rigidity.
  • FIG. 5 shows the central casing 20a, but the side casings 2bL and 2bR are similarly provided with a meat fillet 20e and a partition wall 20c.
  • the lubricating oil scattered on the inner wall surface of the speed reducer casing 20 flows down along the inner wall surface, but the lubricating oil accumulates in the meat thinning 20e on the inner wall surface.
  • a notch 20d for supplying the lubricating oil remaining in the fillet 20e to the rolling bearings 28a, 34a, and 37a is formed in the partition wall 20c located above the bearing fitting holes 35a, 32a, and 27a.
  • the lubricating oil discharged from the notch 20d is guided to the communication groove 45, and the lubricating oil is supplied from the communication groove 45 to the rolling bearings 28a, 34a, 37a.
  • Lubricating oil collected in the three upper fillets 20e is supplied to the bearing fitting holes 27a through the notches 20d. That is, the lubricating oil collected in 20e1 in the figure is sent from the notch 20d to the adjacent meat fillet 20e2, and is sent from the cutout 20d to the adjacent meat thinning 20e3 together with the lubricating oil collected in the meat fillet 20e.
  • the notch 20d provided in the meat fillet 20e is connected to the communication groove 45, and the lubricating oil accumulated in the three meat fillets 20e1, 20e2, 20e3 from the notch 20d is supplied from the communication groove 45 to the rolling bearing 28a.
  • Lubricating oil collected in the upper four meat fillets 20e is supplied to the bearing fitting holes 32a through the notches 20d.
  • the lubricating oil accumulated in 20e4 in the figure is sent from the notch 20d to the adjacent meat fillet 20e6, and the lubricating oil accumulated in the meat fillet 20e5 is sent from the cutout 20d to the lower meat fillet 20e6.
  • the lubricating oil sent from the meat fillet 20e4 and the meat fillet 20e5 is sent from the cutout 20d to the adjacent meat fillet 20e7 together with the lubricant accumulated in the meat fillet 20e6.
  • the notch 20d provided in the meat fillet 20e7 is connected to the communication groove 45, and the lubricating oil accumulated in the four meat fillets 20e4, 20e5, 20e6, and 20e7 from the notch 20d is supplied from the communication groove 45 to the rolling bearing 34a.
  • Lubricating oil collected in the upper three fillets 20e is supplied to the bearing fitting holes 35a through the notches 20d. That is, the lubricating oil collected in 20e8 in the figure is sent from the notch 20d to the adjacent meat fillet 20e9, and is sent from the cutout 20d to the adjacent meat thinning 20e10 together with the lubricating oil collected in the meat fillet 20e.
  • the cutout 20d provided in the meat fillet 20e10 is connected to the communication groove 45, and the lubricating oil accumulated in the three fillets 20e8, 20e9, and 20e10 from the cutout 20d is supplied from the communication groove 45 to the rolling bearing 37a.
  • the lubricating oil accumulated in the fillet 20e can be flowed to the rolling bearing side, and the lubricating oil can be efficiently supplied to the gears and the rolling bearing by circulating the oil bath.
  • the notch 20 d is provided in the partition wall 20 c above the communication groove 45. And since the partition 20c is provided in order to ensure rigidity, it is preferable to provide in the position which avoided the stress load area
  • the lower part of the meat fillet 20e is formed in a tapered shape so that the accumulated lubricating oil can easily flow out.
  • the taper angle ⁇ may be about 5 to 10 degrees. Normally, in the cast product, the draft angle is about 1.5 degrees, but the taper angle ⁇ is larger than that to improve the flow of the lubricating oil. Since the taper of the lower part of the meat fillet 20 is not less than the draft required for the casing, there is no concern about cost increase.
  • Lubricating oil can be discharged more efficiently if the cut depth M of the notch 20d is 3 mm or more and is made as large as possible within the range that maintains the strength of the partition wall 20c. Similarly, the lubricating oil can be discharged more efficiently when the length N of the notch 20d is 3 mm or more and is made as large as possible within the range that maintains the strength of the partition wall 20c.
  • the bearing fitting holes 27a, 32a, and 35a of the central casing 20a have been described.
  • the bearing fitting holes 27b, 32b, and 35b of the side casings 20bL and 20bR are similarly provided with the respective bearing fitting holes.
  • One or more communication grooves 45 that allow the gear space G1 and the internal space G2 to communicate with each other are provided on the inner peripheral surface.
  • the partition wall 20c is provided with a notch 20d, and the lubricating oil discharged from the notch 20d is guided to the communication groove 45, and the lubricating oil is supplied from the communication groove 45 to the rolling bearings 28b, 34b, and 37b.
  • the outer ring 41 may be deformed by a load acting on the outer ring 41 via the rolling element 42.
  • the roundness of the outer ring raceway surface may deteriorate and adversely affect vibration / sound and durability. This load is also applied as a stress load to the partition wall 20c.
  • FIG. 6 shows the arrangement of the gears 24L and 25L.
  • the input gear shaft 23L is positioned in front of the vehicle from the output gear shaft 25L, and the intermediate gear shaft 24L is positioned below the input gear shaft 23L and the output gear shaft 25L.
  • the speed reducer 2R is in a relation in which FIG. 6 is mirror-symmetrical. As shown in FIG.
  • FIG. 6 shows in which direction the load action line is generated.
  • FIG. 5 shows in which direction the load action line is generated.
  • the communication groove 45 is provided on the inner peripheral surface of the bearing fitting hole of the reduction gear casing 20 so that the line of action of the load acting on the rolling bearing and the communication groove 45 do not intersect.
  • the notch 20d formed in the partition wall 20c is also provided at a position that does not intersect the line of action of the load acting on the rolling bearing.
  • the load action line is defined below.
  • a gear meshing row formed by the input gear 23a and the large-diameter gear 24a is designated as A row
  • a gear meshing row constituted by the small-diameter gear 24b and the output gear 25a is designated as the B row.
  • the axis of the input gear shaft 23L is x
  • the axis of the intermediate gear shaft 24L is y
  • the axis of the output gear shaft 25L is z.
  • L1A and L2A are perpendicular to the straight line connecting the axial center x and the axial center y, and are straight lines passing through the axial center x and the axial center y, respectively.
  • L2B and L3B are perpendicular to the straight line connecting the axis y and the axis z, and are straight lines passing through the axis y and the axis z, respectively.
  • L1D is an action line of a load acting on the rolling bearings 28a and 28b of the input gear shaft 23L during acceleration (drive side) due to the meshing of the input gear 23a and the large-diameter gear 24a, that is, the meshing of the gear train A. .
  • the action line of the load acting on the rolling bearings 34a, 34b of the intermediate gear shaft 24L during acceleration (drive side) due to the meshing of the gear train A with the input gear 23a and the large diameter gear 24a is L2DA.
  • L3D is a line of action of a load acting on the rolling bearings 37a and 37b of the output gear shaft 25L during acceleration (drive side) due to the meshing of the gear train B of the small diameter gear 24b and the output gear 25a.
  • L3C is a line of action of a load acting on the rolling bearings 37a and 37b of the output gear shaft 25L during deceleration (coast side) due to the meshing of the gear train B of the small diameter gear 24b and the output gear 25a.
  • An angle ⁇ is formed between L1D and L1A and between L1C and L1A.
  • An angle ⁇ is formed between L2DA and L2A and between L2CA and L2A.
  • An angle ⁇ ′ is formed between L2DB and L2B and between L2CB and L2B.
  • An angle ⁇ ′ is formed between L3D and L3B and between L3C and L3B.
  • angles ⁇ and ⁇ ′ are given by the following equations based on the tooth surface pressure angle and the tooth surface torsion angle of the gear.
  • ⁇ and ⁇ ′ are tooth surface pressure angles
  • ⁇ and ⁇ ′ are tooth surface torsion angles.
  • the action line of the load can be defined by the axial center position and the gear specifications (pressure angle and torsion angle).
  • at least one communication groove 45 is formed at a position not intersecting with the load acting line obtained by the shaft center position and the gear specifications (pressure angle and torsion angle), and the gear space G1 and the internal space G2 are communicated. I am letting.
  • the notch 20d provided in the partition wall 20c is also provided at a position that does not intersect the load acting line obtained by the axial center position and the gear specifications (pressure angle and torsion angle).

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Details Of Gearings (AREA)
PCT/JP2017/001453 2016-02-08 2017-01-18 車両駆動装置 WO2017138312A1 (ja)

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DE202019103779U1 (de) * 2019-07-09 2020-10-12 Hofer Powertrain Innovation Gmbh Twin-Getriebe mit einer vorteilhaften Ölschmierung durch ein Mehrkammernsystem
WO2021005186A1 (de) 2019-07-09 2021-01-14 Hofer Powertrain Innovation Gmbh Getriebe, insbesondere twin-getriebe, und lagerbrille mit einer vorteilhaften ölschmierung durch ein mehrkammernsystem sowie geeignetes verfahren zum schmieren eines solchen getriebes
CN113752807A (zh) * 2020-06-04 2021-12-07 瑞伟安知识产权控股有限公司 具有嵌套轴的电动车辆动力系组件
CN114144602A (zh) * 2019-07-09 2022-03-04 浩夫尔动力总成有限公司 双变速器
US11635130B2 (en) 2020-06-04 2023-04-25 Rivian Ip Holdings, Llc Electric vehicle powertrain assembly having nested shafts

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WO2021005186A1 (de) 2019-07-09 2021-01-14 Hofer Powertrain Innovation Gmbh Getriebe, insbesondere twin-getriebe, und lagerbrille mit einer vorteilhaften ölschmierung durch ein mehrkammernsystem sowie geeignetes verfahren zum schmieren eines solchen getriebes
EP3784929A1 (de) * 2019-07-09 2021-03-03 hofer powertrain innovation GmbH Getriebe, insbesondere twin-getriebe, und lagerbrille mit einer vorteilhaften ölschmierung durch ein mehrkammernsystem sowie geeignetes verfahren zum schmieren eines solchen getriebes
CN114080520A (zh) * 2019-07-09 2022-02-22 浩夫尔动力总成有限公司 变速器、特别是对式变速器和通过多腔系统进行有利的油润滑的轴承托架以及适于润滑变速器的方法
CN114144602A (zh) * 2019-07-09 2022-03-04 浩夫尔动力总成有限公司 双变速器
DE202019103779U1 (de) * 2019-07-09 2020-10-12 Hofer Powertrain Innovation Gmbh Twin-Getriebe mit einer vorteilhaften Ölschmierung durch ein Mehrkammernsystem
EP4385779A2 (de) 2019-07-09 2024-06-19 hofer powertrain innovation GmbH Getriebe, insbesondere twin-getriebe, und lagerbrille mit einer vorteilhaften ölschmierung durch ein mehrkammernsystem sowie geeignetes verfahren zum schmieren eines solchen getriebes
EP4385779A3 (de) * 2019-07-09 2024-08-21 hofer powertrain innovation GmbH Getriebe, insbesondere twin-getriebe, und lagerbrille mit einer vorteilhaften ölschmierung durch ein mehrkammernsystem sowie geeignetes verfahren zum schmieren eines solchen getriebes
CN113752807A (zh) * 2020-06-04 2021-12-07 瑞伟安知识产权控股有限公司 具有嵌套轴的电动车辆动力系组件
EP3919304A1 (en) * 2020-06-04 2021-12-08 Rivian IP Holdings, LLC Electric vehicle powertrain assembly having nested shafts
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US11635130B2 (en) 2020-06-04 2023-04-25 Rivian Ip Holdings, Llc Electric vehicle powertrain assembly having nested shafts
US12384232B2 (en) 2020-06-04 2025-08-12 Rivian Ip Holdings, Llc Electric vehicle powertrain assembly having nested shafts

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