JP2019142312A - Vehicle driving device - Google Patents

Abstract

To reliably supply lubricating oil to a bearing of an intermediate gear positioned in a narrow space by means of a simple structure.SOLUTION: An in-wheel motor driving device 21 comprises an electric motor for driving a wheel, a balanced shaft gear reducer 23 which decelerates and outputs rotation of the electric motor, and a casing 25 housing a parallel axis gear reducer 23. A bearing 41 for rotatably supporting an intermediate gear 33 of the parallel axis gear reducer 23 is installed on a wall surface 55 of the casing 25. An addendum outer diameter of the intermediate gear 33 is larger than an outer ring outer diameter of the bearing 41. The bearing 41 is disposed in a narrow space between the wall surface 55 of the casing 25 and an end surface of a recessed part of the intermediate gear 33. An addendum of the intermediate gear 33 is proximal to a top surface 58 of the casing 25, and a recessed part 59 for collecting lubricating oil scattered by rotation of the intermediate gear 33 is formed in a portion of the top surface 58 of the casing 25 above the bearing.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a vehicle drive device that, for example, inputs a rotational driving force of an electric motor to a reduction gear, reduces the rotational speed, and transmits the reduced speed to a wheel bearing.

  As one type of conventional vehicle drive devices, for example, there is an in-wheel motor drive device (electric drive unit) disclosed in Patent Document 1.

  The in-wheel motor drive device of Patent Document 1 includes an electric motor that generates a driving force for a wheel, and a speed reducer that decelerates and outputs the rotation of the electric motor, and the wheel is driven to rotate by the rotation output of the electric motor. Is configured to do.

  This in-wheel motor drive device has a structure in which an electric motor and a speed reducer are integrally accommodated in a casing.

  The electric motor includes a stator fixed to a casing, a rotor that is rotatably supported by the casing inside the stator, and a rotor shaft that outputs the rotation of the rotor.

  The speed reducer includes a parallel shaft gear train and a planetary gear mechanism. The parallel shaft gear train transmits the rotation of the rotor shaft of the electric motor to the planetary gear mechanism by performing a first stage reduction with respect to the output shaft. The planetary gear mechanism transmits the rotation of the rotor shaft of the electric motor to the output shaft by performing a second-stage deceleration.

JP2015-147491A

  By the way, the in-wheel motor drive device disclosed in Patent Document 1 includes a reduction gear that decelerates by a parallel shaft gear train and a planetary gear mechanism, and by bringing the parallel shaft gear train and the planetary gear mechanism close to each other in the axial direction. The whole unit is reduced in the axial direction.

  On the other hand, in this type of in-wheel motor drive device, lubricating oil for cooling the electric motor and cooling and lubricating the speed reducer is enclosed in a casing. With this lubricating oil, the electric motor is cooled, and the speed reducer is cooled and lubricated by splashing by rotation of each gear of the parallel shaft gear train and the planetary gear mechanism.

  As described above, in the in-wheel motor drive device, by reducing the size of the entire unit in the axial direction, internal parts constituting the in-wheel motor drive device, in particular, the gears constituting the reducer are narrowed in the reducer case. It will be installed in a simple space.

  For this reason, in the case of a bearing that rotatably supports the gear with respect to the reduction gear case and is disposed close to the gear, the lubricating oil is blown off by the rotating gear, making it difficult to reach the bearing. The durability of the bearing may be reduced due to insufficient lubrication.

  In addition, since the amount of lubricating oil adhering to the inner wall surface of the reducer case close to the bearing is small, it is difficult to sufficiently lubricate the bearing with a small amount of lubricating oil. May decrease.

  Accordingly, the present invention has been proposed in view of the above-described problems, and an object of the present invention is to drive a vehicle that can reliably supply lubricating oil to a gear bearing disposed in a narrow space with a simple structure. To provide an apparatus.

  A vehicle drive device according to the present invention includes a structure including an electric motor that drives a wheel, a speed reducer that decelerates and outputs rotation of the electric motor, and a casing that houses the speed reducer.

  In this vehicle drive device, a bearing that rotatably supports a gear of a reduction gear is attached to a wall surface of a casing, an outer diameter of a tooth tip of the gear is larger than an outer diameter of an outer ring of the bearing, and a wall surface of the casing and an end surface of the gear are It has a structure in which bearings are arranged in a narrow space between them.

  As a technical means for achieving the above-described object, the present invention is configured such that the gear tip of the gear is close to the top surface of the casing, and the lubricating oil scattered by the rotation of the gear is applied to the upper portion of the bearing on the top surface of the casing. A concave portion to be retained is formed.

  In the present invention, the concave portion is provided in the upper portion of the bearing on the top surface where the tooth tips of the gear are close to each other, so that the lubricating oil scattered by the rotating gear stays in the concave portion. Thereby, the amount of lubricating oil flowing down from the top surface of the casing to the bearing through the wall surface increases.

  As a result, even if the bearing of the gear attached to the wall surface of the casing is arranged close to the end surface of the gear in a narrow space between the wall surface of the casing and the end surface of the gear, the amount of lubricating oil flowing down to the bearing With this increase, sufficient lubricating oil can be reliably supplied to the gear bearing.

  The recess in the present invention is preferably formed so as to extend in the axial direction of the gear and is inclined downward toward the wall surface of the casing.

  If such a structure is employed, the lubricating oil staying in the recess on the top surface of the casing can easily flow down toward the wall surface of the casing. Therefore, sufficient lubricating oil can be supplied to the gear bearing more reliably.

  The recess in the present invention preferably has a structure formed with a width dimension that overlaps at least a part of the outer diameter of the outer ring of the bearing.

  If such a structure is adopted, at least a part of the bearing is located immediately below the recess. Thereby, the lubricating oil flowing down from the concave portion of the top surface of the casing through the wall surface can be more reliably supplied to the gear bearing.

  In the present invention, a structure in which ribs extending from both sides of the recess to the bearing side are provided on the wall surface of the casing is desirable.

  If such a structure is employ | adopted, the lubricating oil which flows down along a wall surface from the recessed part of the top | upper surface of a casing can be guide | induced to the bearing of a gearwheel along a rib. With this rib, the lubricating oil flowing down from the concave portion of the top surface of the casing through the wall surface can be more reliably supplied to the gear bearing.

  In the present invention, it is desirable to have a structure in which an oil groove for allowing the lubricating oil to flow into the bearing is formed in the lower portion of the concave portion of the bearing support portion provided on the wall surface of the casing.

  If such a structure is adopted, the lubricating oil flowing down from the concave portion of the top surface of the casing along the wall surface flows into the oil groove of the bearing support portion. With this oil groove, the lubricating oil flowing down from the concave portion of the top surface of the casing through the wall surface can be more reliably supplied to the gear bearing.

  According to the present invention, even if the gear bearing provided on the wall surface of the casing is disposed close to the end surface of the gear in a narrow space between the wall surface of the casing and the end surface of the gear, By increasing the amount of lubricating oil flowing down, sufficient lubricating oil can be reliably supplied to the gear bearing.

  As a result, the durability of the bearing can be improved, and a highly reliable long-life vehicle drive device can be provided.

In embodiment of this invention, it is sectional drawing which shows the whole structure of an in-wheel motor drive device. FIG. 2 is a cross-sectional view of the parallel shaft gear reducer (input gear, intermediate gear, and output gear) of FIG. 1 viewed from the wheel side. In embodiment of this invention, it is a principal part expanded sectional view which shows a casing, an intermediate | middle gear, and its bearing. It is principal part expanded sectional drawing which shows a casing, an intermediate | middle gear, and its bearing in other embodiment of this invention. It is a fragmentary sectional view which shows an example of the positional relationship of the bearing of an intermediate gear, and the recessed part of a casing. It is a fragmentary sectional view which shows the other example of the positional relationship of the bearing of an intermediate gear, and the recessed part of a casing. It is a fragmentary sectional view which shows the other example of the positional relationship of the bearing of an intermediate gear, and the recessed part of a casing. It is a fragmentary sectional view which shows the structural example which provided the rib in the wall surface of the casing. It is a fragmentary sectional view which shows the structural example which provided the oil groove in the bearing support part of the intermediate | middle gear. It is a top view which shows schematic structure of the electric vehicle carrying an in-wheel motor drive device. It is back sectional drawing which shows the electric vehicle of FIG.

  An in-wheel motor drive device will be described in detail with reference to the drawings as an embodiment of the present invention. FIG. 10 is a schematic plan view of the electric vehicle 11 on which the in-wheel motor drive device 21 is mounted, and FIG. 11 is a schematic cross-sectional view of the electric vehicle 11 as viewed from the rear.

  As shown in FIG. 10, the electric vehicle 11 includes a chassis 12, a front wheel 13 as a steering wheel, a rear wheel 14 as a drive wheel, and an in-wheel motor drive device 21 that transmits driving force to the rear wheel 14. Equip.

  As shown in FIG. 11, the rear wheel 14 is accommodated in a wheel housing 15 of the chassis 12 and is fixed to a lower portion of the chassis 12 via an independent suspension type suspension device (suspension) 16.

  The electric vehicle 11 includes an in-wheel motor drive device 21 that independently drives the left and right rear wheels 14 inside the wheel housing 15. This eliminates the need to provide a motor, a drive shaft, and a differential gear mechanism on the chassis 12.

  As a result, the electric vehicle 11 has an advantage that a large cabin space can be secured and the rotation of the left and right rear wheels 14 can be controlled independently.

  On the other hand, in the electric vehicle 11, it is necessary to suppress unsprung weight in order to improve running stability and NVH characteristics. Furthermore, in order to secure a large cabin space, the in-wheel motor drive device 21 is required to be downsized.

  Therefore, the in-wheel motor drive device 21 of the embodiment shown in FIG. 1 has the following structure. Thereby, the compact in-wheel motor drive device 21 is implement | achieved and the electric vehicle 11 excellent in driving | running | working stability and NVH characteristic is obtained by suppressing unsprung weight.

  Before describing the characteristic configuration of this embodiment, the overall configuration of the in-wheel motor drive device 21 will be described. In the following description, with the in-wheel motor drive device 21 mounted on the vehicle body, the side closer to the outside of the vehicle body is referred to as the outboard side (left side in the drawing), and the side closer to the center is inboard side (right side in the drawing). Called.

  As shown in FIG. 1, the in-wheel motor drive device 21 includes an electric motor 22 that drives the rear wheel 14 (see FIGS. 10 and 11), and a parallel shaft gear reducer that decelerates and outputs the rotation of the electric motor 22. 23 and a wheel bearing 24 for transmitting the output of the parallel shaft gear reducer 23 to the rear wheel 14 described above.

  In this embodiment, the radial gap type electric motor 22 is illustrated, but other electric motors such as an axial gap type may be used.

  The electric motor 22 and the parallel shaft gear reducer 23 are accommodated in the casing 25. The casing 25 in which the electric motor 22 and the parallel shaft gear reducer 23 are accommodated is attached in the wheel housing 15 (see FIG. 11) of the electric vehicle 11.

  The electric motor 22 includes a stator 26 fixed to the casing 25, a rotor 27 disposed so as to face the inner side in the radial direction of the stator 26 with a gap, and a rotor 27 disposed on the inner side in the radial direction of the rotor 27 so as to rotate integrally with the rotor 27. And a motor rotating shaft 28.

  The motor rotating shaft 28 can rotate at a high speed of about 10,000 to 1000 rotations per minute. The stator 26 is configured by winding a coil around the outer periphery of the magnetic core. The rotor 27 has a permanent magnet or a magnetic body disposed therein.

  The motor rotating shaft 28 holds the rotor 27 by a holder portion 29 extending radially outward. The motor rotating shaft 28 is supported by the bearings 30 and 31 so as to be rotatable with respect to the casing 25.

  The parallel shaft gear reducer 23 includes an input gear 32, an intermediate gear 33, and an output gear 34. The intermediate gear 33 has a large-diameter tooth portion 35 on the inboard side and a small-diameter tooth portion 36 on the outboard side coaxially.

  In the parallel shaft gear reducer 23, the tooth portion 37 of the input gear 32 meshes with the large diameter tooth portion 35 of the intermediate gear 33, and the small diameter tooth portion 36 of the intermediate gear 33 meshes with the tooth portion 38 of the output gear 34. Thus, the rotation of the electric motor 22 is decelerated with a predetermined reduction ratio.

  Since the in-wheel motor drive device 21 is housed inside the wheel housing 15 (see FIG. 11) and becomes an unsprung load, a reduction in size and weight is essential.

  Therefore, by using the parallel shaft gear reducer 23 having a large reduction ratio, the electric motor 22 can be miniaturized by combining with the high-speed electric motor 22, and the in-wheel motor drive device 21 having a compact and high reduction ratio can be obtained. Can be realized.

  The input gear 32 is coaxially attached to the motor rotating shaft 28 by spline fitting. The input gear 32, the intermediate gear 33, and the output gear 34 are rotatably supported on the casing 25 by bearings 39 to 44. The output gear 34 is coaxially attached to the hub wheel 46 of the wheel bearing 24 by spline fitting.

  FIG. 2 is a cross-sectional view of the input gear 32, the intermediate gear 33, and the output gear 34 of the parallel shaft gear reducer 23 as seen from the outboard side. The rotation centers C1 to C3 of the input gear 32, the intermediate gear 33, and the output gear 34 are offset with the positional relationship shown in FIG.

  As described above, the input gear 32, the intermediate gear 33, and the output gear 34 are offset to reduce the size of the parallel shaft gear reducer 27 in the axial direction and the radial direction.

  Here, helical gears are used for the input gear 32, the intermediate gear 33, and the output gear 34. Helical gears are effective in that the number of teeth engaged simultaneously increases and the tooth contact is dispersed, so that the sound is quiet and torque fluctuation is small.

  In this way, by using a helical gear as the parallel shaft gear reducer 23, it is possible to realize the in-wheel motor drive device 21 that is easy to manufacture and can be reduced in cost, and that is quiet and efficient in terms of performance. it can.

  The wheel bearing 24 includes an outer ring 45 fixed to the casing 25, a hub ring 46 disposed inside the outer ring 45, an inner ring 47 press-fitted into the hub ring 46, a hub ring 46, the inner ring 47, and the outer ring 45. The main part is composed of a plurality of rolling elements 48 arranged therebetween.

  A preload is applied to the wheel bearing 24 by crimping the end portion on the inboard side of the hub wheel 46. By applying this preload, the wheel bearing 24 has a double-row angular ball bearing structure.

  A shaft portion 50 extending integrally from the output gear 34 of the parallel shaft gear reducer 23 to the outboard side is coupled to the shaft hole 49 of the hub wheel 46 of the wheel bearing 24 so as to transmit torque by spline fitting. .

  Seal members 51 are provided at both ends in the axial direction of the wheel bearing 24 to prevent intrusion of muddy water and the like and leakage of grease.

  A flange 52 is integrally formed on the outboard side of the hub wheel 46. The rear wheel 14 (see FIGS. 10 and 11) is connected to the flange 52 with a hub bolt (not shown).

  In the in-wheel motor drive device 21 configured as described above, the rotation of the electric motor 22 is decelerated by the input gear 32, the intermediate gear 33 and the output gear 34 of the parallel shaft gear reducer 23 and transmitted to the wheel bearing 24.

  Since the rotation of the electric motor 22 is decelerated by the parallel-shaft gear reducer 23 and transmitted to the wheel bearing 24, the rear wheel 14 (see FIGS. 10 and 10) even when the low-torque high-speed electric motor 22 is employed. 11) can be transmitted.

  The overall configuration of the in-wheel motor drive device 21 in this embodiment is as described above, and the characteristic configuration will be described in detail below.

  In the in-wheel motor drive device 21, lubricating oil for cooling the electric motor 22 and cooling and lubricating the parallel shaft gear reducer 23 is enclosed in the internal space of the casing 25.

  In particular, as shown in FIG. 2, an oil bath state in which a part of the tooth portion 38 of the output gear 34 is constantly immersed in the lubricating oil 53 is set, and the parallel shaft gear reducer 23 is moved by splashing by the rotation of the output gear 34. Cool and lubricate.

  In this way, by immersing only the output gear 34 having the slowest rotation speed, there is an effect of avoiding a reduction in efficiency of the parallel shaft gear reducer 23 due to an increase in the stirring resistance of the lubricating oil 53.

  Here, in order to reduce the weight and size of the in-wheel motor drive device 21, as shown in FIG. 1, the input gear 32, the intermediate gear 33, and the output gear 34 of the parallel shaft gear reducer 23 are closely arranged, The radial gap and the axial gap between the parallel shaft gear reducer 23 and the casing 25 are made as small as possible.

  On the other hand, a pump (not shown) is disposed above the input gear 32, and lubricating oil is dropped from the pump, whereby the input gear 32 and its bearings 39, 40 are cooled and lubricated. On the other hand, as for the intermediate gear 33, it is difficult in terms of space to arrange a pump like the input gear 32 described above.

  Further, for the intermediate gear 33 having the large-diameter tooth portion 35 having a tooth tip outer diameter larger than the outer diameter of the bearing outer ring, the bearing 41 on the inboard side is accommodated in the concave portion 54 of the large-diameter tooth portion 35. Thereby, size reduction in the axial direction of the parallel shaft gear reducer 23 is achieved.

  As a result, the bearing 41 on the inboard side is disposed in a narrow space 57 between the wall surface 55 of the casing 25 and the concave end surface 56 of the large-diameter tooth portion 35 of the intermediate gear 33. The lubricating oil 53 splashed by the rotation and the lubricating oil 53 attached to the wall surface 55 of the casing 25 are difficult to reach.

  In this parallel shaft gear reducer 23, the bearing 41 of the intermediate gear 33 whose outer diameter of the large-diameter tooth portion 35 is larger than the outer diameter of the outer ring of the bearing 41 includes the wall surface 55 of the casing 25 and the concave end face 56 of the intermediate gear 33. It is arranged in a narrow space 57 between the two.

  Therefore, as shown in FIG. 2, the parallel shaft gear reducer 23 according to this embodiment has an intermediate intermediate shaft 33 on the upper part of the bearing outer ring on the top surface 58 of the casing 25 where the teeth of the large-diameter tooth portion 35 of the intermediate gear 33 are close to each other. A structure is provided in which a recess 59 for retaining the lubricating oil 53 scattered by the rotation of the gear 33 is formed.

  In this parallel shaft gear reducer 23, the recess 59 is provided in the upper part of the bearing of the top surface 58 of the casing 25 where the teeth of the large-diameter tooth portion 35 of the intermediate gear 33 are close to each other. The lubricating oil 53 scattered with force stays in the recess 59. Thereby, the amount of lubricating oil flowing down from the top surface 58 of the casing 25 along the wall surface 55 increases.

  As a result, the bearing 41 of the intermediate gear 33 provided on the wall surface 55 of the casing 25 is placed on the concave end surface 56 of the intermediate gear 33 in a narrow space 57 between the wall surface 55 of the casing 25 and the concave end surface 56 of the intermediate gear 33. Even if they are arranged close to each other, sufficient lubricating oil 53 can be reliably supplied to the bearing 41 of the intermediate gear 33 by increasing the amount of lubricating oil flowing down along the wall surface 55.

  As a result, the durability of the bearing 41 of the intermediate gear 33 can be improved, and a reliable and long-life in-wheel motor drive device 21 can be provided.

  As shown in FIG. 3, the recess 59 of the top surface 58 of the casing 25 is formed so as to extend in the axial direction of the intermediate gear 33, and is inclined downward toward the wall surface 55 of the casing 25.

  By adopting such a structure, the lubricating oil 53 staying in the recess 59 of the top surface 58 of the casing 25 can easily flow down along the wall surface 55 of the casing 25. Therefore, sufficient lubricating oil 53 can be reliably supplied to the bearing 41 of the intermediate gear 33.

  In this embodiment, the top surface 58 and the concave portion 59 that are inclined downward toward the wall surface 55 of the casing 25 are illustrated. However, as shown in FIG. 4, the ceiling that extends horizontally toward the wall surface 55 of the casing 25 is illustrated. The surface 58 and the recessed part 60 may be sufficient.

  Even in the structure as shown in FIG. 4, the lubricating oil 53 is sufficiently retained in the recess 59 because the amount of lubricating oil splashed by the centrifugal force generated by the rotation of the intermediate gear 33 is sufficient at the normal traveling speed of the vehicle. To do. Thereby, the lubricating oil 53 flows down from the top surface 58 of the casing 25 along the wall surface 55, and the lubricating oil 53 can be reliably supplied to the bearing 41.

  5, 6, and 7 illustrate the positional relationship between the bearing 41 of the intermediate gear 33 and the recess 59 of the top surface 58 of the casing 25. The intermediate gear 33 is not shown.

  FIG. 5 illustrates a recess 59 formed in the upper portion of the outer ring of the bearing 41 with a width dimension W1 that matches the outer diameter of the outer ring of the bearing 41. As shown in FIGS. 6 and 7, it may be a recess 59 formed with width dimensions W2 and W3 so as to overlap a part of the outer diameter of the outer ring of the bearing 41.

  On the top surface 58 of the casing 25, the recess 59 shown in FIG. 6 is arranged behind the bearing 41 in the rotation direction, and the recess 59 shown in FIG. 7 is arranged ahead of the bearing 41 in the rotation direction. 6 and 7 have width dimensions W2 and W3 that are approximately half the outer diameter of the outer ring of the bearing 41.

  In this way, by forming the recess 59 with the width dimensions W1, W2, W3 so as to overlap at least a part of the outer diameter of the outer ring of the bearing 41, at least a part of the bearing 41 is positioned directly below the recess 59. Become. Thereby, the lubricating oil 53 flowing down from the concave portion 59 of the top surface 58 of the casing 25 along the wall surface 55 can be reliably supplied to the bearing 41 of the intermediate gear 33.

  Furthermore, as shown in FIG. 8, a structure in which ribs 60 extending from both sides of the recess 59 to the support portion 61 of the bearing 41 are provided on the wall surface 55 of the casing 25 is effective. Two ribs 60 shown in the figure are provided on both sides of the recess 59 above the bearing 41, but the number thereof is arbitrary.

  Thereby, the lubricating oil 53 flowing down from the concave portion 59 of the top surface 58 of the casing 25 along the wall surface 55 can be guided to the bearing 41 along the rib 60. With this rib 60, the lubricating oil 53 flowing down from the recess 59 of the casing 25 along the wall surface 55 can be reliably supplied to the bearing 41 of the intermediate gear 33.

  When the lubricating oil 53 flowing down from the recess 59 along the wall surface 55 is guided to the bearing 41, the ribs 60 located on the inner sides on both sides of the recess 59 act particularly effectively, but the ribs located on the outer sides on both sides of the recess 59. 60 also contributes to guiding the overflowing lubricating oil 53 to the bearing 41.

  Further, as shown in FIG. 9, an oil groove 62 for allowing the lubricating oil 53 to flow into the bearing 41 may be provided in the lower portion of the concave portion of the support portion 61 of the bearing 41.

  As a result, the lubricating oil 53 that has flowed down from the concave portion 59 of the top surface 58 of the casing 25 along the wall surface 55 flows into the oil groove 62 of the support portion 61. By this oil groove 62, the lubricating oil 53 that has flowed down from the recess 59 of the casing 25 along the wall surface 55 can be reliably supplied to the bearing 41 of the intermediate gear 33.

  In the above embodiment, the vehicle drive device provided with the in-wheel motor drive device 21 for driving the left and right rear wheels 14 inside the wheel housing 15 (see FIG. 11) has been described, but the present invention is limited to this. The present invention can also be applied to a vehicle drive device called an on-board type.

  In this on-board type vehicle drive device, two sets of an electric motor 22 and a parallel shaft gear reducer 23 are attached to the vehicle body, and the output of the parallel shaft gear reducer 23 is transmitted to the rear wheels 14 via the left and right drive shafts. The structure which comprises.

  Alternatively, a structure is provided in which a set of electric motor 22 and parallel shaft gear reducer 23 is attached, the output of parallel shaft gear reducer 23 is distributed to the left and right by a differential gear, and transmitted to rear wheel 14 via a drive shaft.

  Further, in the above embodiment, as shown in FIGS. 10 and 11, the electric vehicle 11 having the rear wheel 14 as the driving wheel is illustrated, but the front wheel 13 may be the driving wheel, Also good. In the present specification, “electric vehicle” is a concept including all vehicles that obtain driving force from electric power, and includes, for example, a hybrid vehicle.

  The present invention is not limited to the above-described embodiments, and can of course be implemented in various forms without departing from the gist of the present invention. It includes the equivalent meanings recited in the claims and the equivalents recited in the claims, and all modifications within the scope.

21 In-wheel motor drive device 22 Electric motor 23 Reducer (parallel shaft gear reducer)
24 Wheel Bearing 25 Casing 33 Gear (Intermediate Gear)
41 Bearing 55 Wall 56 End surface 57 Space 58 Top 59 Recess 60 Rib 61 Bearing support 62 Oil groove

Claims (5)

A vehicle drive device comprising: an electric motor that drives a wheel; a speed reducer that decelerates and outputs rotation of the electric motor; and a casing that houses the speed reducer,
A bearing that rotatably supports the gear of the speed reducer is attached to the wall surface of the casing, and an outer diameter of a tooth tip of the gear is larger than an outer diameter of the outer ring of the bearing, and the wall surface of the casing and the end surface of the gear The bearing is arranged in a narrow space between,
A vehicle drive characterized in that a tooth tip of the gear is close to the top surface of the casing, and a recess is formed in the upper portion of the bearing on the top surface of the casing to retain the lubricant scattered by the rotation of the gear. apparatus.   The vehicle drive device according to claim 1, wherein the recess is formed so as to extend in an axial direction of the gear and is inclined downward toward a wall surface of the casing.   The vehicle drive device according to claim 1, wherein the recess is formed with a width dimension so as to overlap with at least a part of an outer ring outer diameter of the bearing.   The vehicle drive device according to any one of claims 1 to 3, wherein a rib extending from both sides of the concave portion to the bearing side is provided on a wall surface of the casing.   The vehicle drive device according to any one of claims 1 to 4, wherein an oil groove for allowing lubricating oil to flow into the bearing is formed in a lower portion of a concave portion of a bearing support portion provided on a wall surface of the casing.

Images