JP6196946B2 - Lubrication structure of bearing - Google Patents

Description

  The present invention relates to a lubricating structure for a bearing.

  As a conventional lubrication structure for a bearing, in Patent Document 1, as shown in FIG. 12, a bearing supporting boss 102 of a side cover 101 is provided with an oil passage portion 104 that guides lubricating oil to the bearing 103, and is supported by the bearing 103. A rib 106 extending from the bearing support boss 102 in the peripheral direction of the side cover 101 is provided on the side cover 101 at a position immediately after the oil passage portion in the rotation direction of the gear 105, and is further provided at the oil passage portion position of the bearing support boss 102. It is described that a guide plate 107 is provided. With this configuration, when the gear 105 rotates, oil droplets scattered in the rotation direction of the gear 105 collide with the rib 106 and flow down along the rib 106, and are formed by the rib 106, the guide plate 107, and the bearing support boss 102. It is described that the bearing 103 is stored in the recessed portion 108 and lubricated through the oil passage portion 104.

Japanese Utility Model Publication No. 62-46857

  However, according to the lubrication structure of the bearing described in Patent Document 1, since the rib 106 protrudes from the wall surface of the side cover 101, the flow speed of the lubricating oil scraped up by the gear 105 rotating at a high speed increases. Then, there is a risk that the lubricating oil will strongly collide with the rib 106 and bubbles may be generated or noise / vibration may occur. In addition, since most of the lubricated oil is supplied to the bearing 103 via the oil passing portion 104, there is a possibility that the return of the lubricating oil to the storage portion may be delayed.

  The present invention has been made in view of the above problems, and an object of the present invention is to provide a bearing lubrication structure capable of suppressing the generation of bubbles and the generation of noise and vibration.

In order to achieve the above object, the invention described in claim 1
A rotating body (for example, first and second planetary gear speed reducers 12A and 12B in an embodiment described later);
Bearings that rotatably support the rotating body (for example, second bearings 33A and 33B in the embodiments described later),
A wall portion (for example, partition walls 18A and 18B in an embodiment described later) on which the bearing is disposed, and a storage portion (for example, a storage portion RT in an embodiment described later) for storing a lubricating fluid for lubrication of the bearing. And a housing for housing the rotating body (for example, a case 11 in an embodiment described later), and a bearing lubrication structure,
The wall portion is disposed adjacent to the rotating body on one side of the rotating body (for example, the outer side in an embodiment described later) in the rotation axis direction of the rotating body,
The rotating body is arranged so that a part of the lower part in the vertical direction is immersed in the storage part,
The wall portion is a concave portion (for example, a concave portion in an embodiment described later) formed in a facing surface facing the rotating body (for example, a surface 82 in an embodiment described later) in a direction away from the rotating body. 84)
The concave portion is formed over a region having a predetermined length in the radial direction and the circumferential direction on the outer side in the radial direction than the bearing as viewed from the rotational axis direction ,
The wall portion is a second convex portion (e.g., formed on a back surface (e.g., a back surface 93 in an embodiment described later) opposite to the facing surface so as to extend radially outward from the rotation axis. A convex rib 94) in an embodiment to be described later,
The concave portion is formed between two second convex portions adjacent to each other in the circumferential direction.

Moreover, in addition to the structure of Claim 1, the invention of Claim 2 is
Of the facing surface, when a region adjacent to the concave portion in the circumferential direction and not formed with the concave portion is defined as another portion (for example, the other portion 83 in the embodiment described later), the other portion of the concave portion. An upper boundary portion (for example, a first step portion 85a in an embodiment described later) located above the boundary portion is formed in a step shape having a predetermined length in the rotation axis direction.

Moreover, in addition to the structure of Claim 2, the invention of Claim 3 is
The upper boundary portion extends in a direction intersecting the horizontal direction.

Moreover, in addition to the structure of any one of Claims 1-3, invention of Claim 4 is provided.
The wall portion includes a convex portion (for example, a protrusion portion 86 in an embodiment described later) that protrudes from the concave portion in a direction approaching the rotating body.

Moreover, in addition to the structure of Claim 4, the invention of Claim 5 adds to the structure of Claim 4,
The convex portion extends in a direction intersecting the horizontal direction.

In addition to the configuration described in claim 4 or 5, the invention described in claim 6
Of the opposing surface, when the region adjacent to the concave portion in the circumferential direction and not formed with the concave portion is defined as another portion (for example, the other portion 83 in the embodiment described later), the convex portion is The end on the rotating body side of the convex portion is formed so as not to protrude from the other portion.

Moreover, in addition to the structure of any one of Claims 1-6, invention of Claim 7 is provided,
When a region of the opposing surface that is adjacent to the concave portion in the circumferential direction and is not formed with the concave portion is defined as another portion (for example, another portion 83 in an embodiment described later), the other portion is the circle. It has a smooth surface that is smoothly formed over a region having a predetermined length in the circumferential direction.

Moreover, in addition to the structure of any one of Claims 1-7, invention of Claim 8 is provided,
The facing surface includes an inclined surface forming a conical inclined surface of a virtual cone having a vertex on the rotation axis in a direction away from the rotating body over a region having a predetermined length in the circumferential direction,
The concave portion is formed on the inclined surface.

Moreover, in addition to the structure as described in any one of Claims 1-8 , invention of Claim 9 is provided,
The wall portion is provided on a back surface (for example, a back surface 93 in an embodiment described later) opposite to the facing surface, and a third convex portion (for example, a shape corresponding to the concave portion at a position corresponding to the concave portion). And a convex portion 95 in an embodiment described later.

The invention according to claim 10 is
A rotating body (for example, first and second planetary gear speed reducers 12A and 12B in an embodiment described later);
Bearings that rotatably support the rotating body (for example, second bearings 33A and 33B in the embodiments described later),
A wall portion (for example, partition walls 18A and 18B in an embodiment described later) on which the bearing is disposed, and a storage portion (for example, a storage portion RT in an embodiment described later) for storing a lubricating fluid for lubrication of the bearing. And a housing for housing the rotating body (for example, a case 11 in an embodiment described later), and a bearing lubrication structure,
The wall portion is disposed adjacent to the rotating body on one side of the rotating body (for example, the outer side in an embodiment described later) in the rotation axis direction of the rotating body,
The rotating body is arranged so that a part of the lower part in the vertical direction is immersed in the storage part,
The wall portion is a concave portion (for example, a concave portion in an embodiment described later) formed in a facing surface facing the rotating body (for example, a surface 82 in an embodiment described later) in a direction away from the rotating body. 84)
The concave portion is formed over a region having a predetermined length in the radial direction and the circumferential direction on the outer side in the radial direction than the bearing as viewed from the rotational axis direction,
The rotating body includes a first rotating body (for example, first and second planetary gear type speed reducers 12A and 12B in an embodiment described later) and a second rotating body (for example, rotors 15A and 15B in an embodiment described later). And including
The wall portion includes a first chamber (for example, a reducer chamber SC in an embodiment described later) that houses the first rotating body and a second chamber (for example, in an embodiment described later) that houses the second rotating body. motor chamber SA, SB) and Ri bulkhead der for partitioning,
The first rotating body is disposed to face the facing surface,
The second rotating body is disposed to face a back surface (for example, a back surface 93 in an embodiment described later) opposite to the facing surface in the rotation axis direction, and is different from the bearing (for example, described later). The first bearings 19A, 19B) in the embodiment to be rotatably supported by the partition wall,
The partition wall is inserted in a radial direction inside through a connecting member (for example, cylindrical shafts 16A and 16B in an embodiment described later) that mechanically connects the first rotating body and the second rotating body in the rotational axis direction. An extending cylindrical portion (for example, an annular protruding wall 88 in an embodiment described later),
The bearing is disposed on the radially outer side of the cylindrical portion, and the other bearing is disposed on the radially inner side of the cylindrical portion,
The cylindrical portion includes a communication path (for example, a gap portion 92 in an embodiment described later) that communicates the radially outer side and the radially inner side.

The invention described in Claim 11, in addition to the configuration according to claim 10,
The concave portion and the communication path are continuous.

Moreover, in addition to the structure of Claim 10 or 11 , the invention of Claim 12 is
The first rotating body is one of a rotor of an electric motor and a transmission mechanically connected to the rotor,
The second rotating body is the other of the rotor and the transmission.

The invention described in Claim 13, in addition to the configuration according to any one of claims 1 to 12
The rotating body is mechanically connected to a wheel (for example, a rear wheel Wr in an embodiment to be described later) of a vehicle (for example, a vehicle 3 in an embodiment to be described later),
In an orthogonal coordinate system in which the rotation axis of the rotating body (for example, the rotation axis X in the embodiment described later) is the origin, the x-axis is the horizontal direction, and the y-axis is the vertical direction,
When the rotating body rotates clockwise in the orthogonal coordinate system when the vehicle moves forward, the concave portion is formed at a position that becomes the second quadrant,
When the rotating body rotates counterclockwise in the orthogonal coordinate system when the vehicle moves forward, the concave portion is formed at a position that is in the first quadrant.

The invention of claim 14, in addition to the configuration according to any one of claims 1 to 13
The rotating body is a left rotating body (for example, an embodiment to be described later) mechanically connected to a left wheel (for example, a left rear wheel LWr in an embodiment to be described later) of a vehicle (for example, a vehicle 3 in an embodiment to be described later). And a right rotating body (for example, a planetary carrier 23B in an embodiment described later) mechanically connected to a right wheel of the vehicle (for example, a right rear wheel RWr in an embodiment described later). Including
The wall portion includes a left wall portion (for example, a partition wall 18A in an embodiment to be described later) disposed in proximity to the left rotating body and a right wall portion (for example, to be described later) disposed in proximity to the right rotating body. Partition 18B) in an embodiment to
The right wall portion is inverted from the left wall portion with respect to an intermediate surface (for example, an intermediate surface M in an embodiment described later) that is orthogonal to the rotational axis direction and is located between the left wall portion and the right wall portion. The left wall portion is reversely moved with respect to the intermediate surface and rotated with respect to the rotation axis.

According to the first aspect of the present invention, a part of the lubricating fluid that is scraped up along with the rotation of the rotating body and is transmitted along the surface of the wall portion is guided radially inward through the concave portion provided in the wall portion. The bearing can be lubricated. In this way, by using the concave part with the lubrication fluid guidance on the wall, it is possible to suppress the generation of bubbles, noise and vibration, and to avoid storing excessive lubrication fluid more than necessary. It can suppress that the return to a part becomes late.
In addition, by forming the second convex portion radially so as to extend in the radial direction, the rigidity of the wall portion can be increased and vibration and noise can be suppressed. Further, since the second convex portion is formed on the back surface instead of the facing surface, the return of excess lubricating fluid that passes through the concave portion to the storage portion is not hindered.

  According to the second aspect of the present invention, more lubricating fluid can be collected when the lubricating fluid hits the upper boundary portion formed in a step shape.

  According to the third aspect of the present invention, more lubricating fluid can be guided radially inward by the upper boundary portion extending in the direction intersecting the horizontal direction.

  According to the invention described in claim 4, more lubricating fluid can be collected by the convex portion.

  According to the fifth aspect of the present invention, more lubricating fluid can be guided radially inward by the convex portions extending in the direction intersecting the horizontal direction.

  According to the sixth aspect of the present invention, it is possible to suppress the lubricated fluid that has been scooped up from hitting the convex portion strongly.

  According to the seventh aspect of the present invention, excess lubricating fluid that has not been collected in the concave portion and has passed through the concave portion can be quickly returned to the storage portion.

  According to the eighth aspect of the present invention, since the concave portion is formed on the inclined surface forming the conical slope of the virtual cone having the apex on the rotation axis in the direction away from the rotating body, the lubricating fluid that propagates through the concave portion More inwardly in the radial direction.

According to the ninth aspect of the present invention, since the opposite surface protrudes to the back as much as the concave surface is provided, the change in the thickness of the wall portion with the other portion where the concave portion is not formed is suppressed, and the local rigidity is reduced. And stress concentration can be suppressed.

According to the tenth aspect of the present invention, a part of the lubricating fluid that is scraped up along with the rotation of the rotating body and is transmitted through the surface of the wall portion is guided radially inward through the concave portion provided in the wall portion. The bearing can be lubricated. In this way, by using the concave part with the lubrication fluid guidance on the wall, it is possible to suppress the generation of bubbles, noise and vibration, and to avoid storing excessive lubrication fluid more than necessary. It can suppress that the return to a part becomes late.
Moreover, since the wall part in which the concave part is formed is not the outer wall constituting the outer shell of the housing but the partition wall that partitions the internal space, the concave part optimal for lubrication can be formed.
In addition to the first rotating body, the second rotating body is also supported by the partition wall, so that the first rotating body and the second rotating body can be arranged closer to each other, and the partition wall can be made thinner.
Further, by arranging the bearing and the other bearing separately on the radially outer side and the inner side of the cylindrical portion, both can be arranged closer to each other in the axial direction. In addition, by forming the communication path in the cylindrical portion, a part of the lubricating fluid that lubricates the bearing can be supplied to the other bearing.

According to the eleventh aspect of the present invention, it is easy to form and more lubricating fluid can be turned to another bearing.

According to the twelfth aspect of the present invention, the lubricating fluid can be scraped up by the rotation of the rotor or the transmission.

According to the thirteenth aspect of the present invention, since the concave portion is positioned above the rotation axis, the lubricating fluid collected in the concave portion can be guided to the bearing using natural fall. Moreover, since the distance from the oil surface to the concave portion is short, more lubricating fluid can be collected in the concave portion.

According to invention of Claim 14 , a left wall part and a right wall part can be made into the same member.

1 is a block diagram showing a schematic configuration of a hybrid vehicle that is an embodiment of a vehicle on which an electric motor according to the present invention can be mounted. It is a longitudinal cross-sectional view of the rear-wheel drive device which concerns on one Embodiment. FIG. 3 is an enlarged partial sectional view of an upper portion of the rear wheel drive device shown in FIG. 2. It is a perspective view which shows the state with which the rear-wheel drive device was mounted in the flame | frame. (A) And (b) is the figure which looked at the partition arrange | positioned inside the case from the axial direction inner side, respectively. It is a perspective view which shows the principal part of a partition. It is sectional drawing which shows the principal part of a partition. It is the figure which made the 2nd bearing unillustrated in FIG. It is the figure which made the 2nd bearing unillustrated in FIG. (A) is a front view of a partition, (b) is a side view of a partition. It is the figure which looked at the partition on the left side arrange | positioned inside the case from the axial direction inner side. It is sectional drawing which shows the principal part of the partition which concerns on a modification.

  The bearing lubrication structure according to the present invention is applied to a vehicle having a drive system as shown in FIG. 1, for example. In the following description, a case where a vehicle drive device having a bearing lubrication structure of the present invention is used for rear wheel drive will be described as an example, but it may be used for front wheel drive.

  A vehicle 3 shown in FIG. 1 is a hybrid vehicle having a drive device 6 (hereinafter referred to as a front wheel drive device) in which an internal combustion engine 4 and an electric motor 5 are connected in series at the front portion of the vehicle. Is transmitted to the front wheels Wf via the transmission 7. On the other hand, the power of the drive device 1 (hereinafter referred to as a rear wheel drive device) that is provided at the rear of the vehicle separately from the front wheel drive device 6 and is not mechanically connected to the front wheel drive device 6 is rear wheel Wr (RWr). , LWr). The electric motor 5 of the front wheel drive device 6 and the first and second electric motors 2A, 2B of the rear wheel drive device 1 are connected to the battery 9 so that power supply from the battery 9 and energy regeneration to the battery 9 are possible. It has become. In FIG. 1, reference numeral 8 denotes a control device for controlling the entire vehicle.

  First, 1st and 2nd electric motor 2A, 2B as a rotary electric machine of one Embodiment which concerns on this invention is demonstrated based on FIGS.

  FIG. 2 is a longitudinal sectional view of the entire rear wheel drive device 1, and FIG. 3 is an enlarged partial sectional view of the upper part of FIG. In the figure, reference numeral 11 denotes a case of the rear wheel drive device 1, and the case 11 is arranged on the left and right of the central case 11 </ b> M so as to sandwich the central case 11 </ b> M between the central case 11 </ b> M and the central case 11 </ b> M. The motor cases 11A and 11B are arranged, and the whole is formed in a substantially cylindrical shape.

  Inside the case 11 are axles 10A and 10B for the rear wheels Wr, first and second motors 2A and 2B for driving the axle, and first and second motors 2A and 2B for decelerating the driving rotation of the first and second motors 2A and 2B. The first and second planetary gear speed reducers 12A and 12B are arranged side by side on the same axis.

  The axle 10A, the first electric motor 2A and the first planetary gear speed reducer 12A drive and control the left rear wheel LWr, and the axle 10B, the second electric motor 2B and the second planetary gear speed reducer 12B drive the right rear wheel RWr. Control. The axle 10A, the first electric motor 2A and the first planetary gear speed reducer 12A, and the axle 10B, the second electric motor 2B and the second planetary gear speed reducer 12B are arranged symmetrically in the vehicle width direction in the case 11. Yes. The left rear wheel LWr is positioned opposite to the first planetary gear type reduction gear 12A with respect to the first electric motor 2A, and the right rear wheel RWr is also connected to the second planetary gear type reduction gear 12B with respect to the second electric motor 2B. Located on the opposite side. The first electric motor 2A and the first planetary gear type speed reducer 12A are arranged in this order from the outer side in the vehicle width direction, and the second electric motor 2B and the second planetary gear type speed reducer 12B are arranged from the outer side in the vehicle width direction. By arrange | positioning in this order, 1st and 2nd planetary gear type reduction gears 12A and 12B are arrange | positioned between 1st and 2nd electric motor 2A, 2B.

  As shown also in FIG. 5, partition walls 18 </ b> A and 18 </ b> B that extend radially inward are fixed to the central case 11 </ b> M side of the motor cases 11 </ b> A and 11 </ b> B, respectively. More specifically, the partition walls 18 </ b> A and 18 </ b> B have a substantially pentagonal shape having a cylindrical hole at the center, and the apexes of the partition walls 18 </ b> A and 18 </ b> B are fastened to the motor cases 11 </ b> A and 11 </ b> B by bolts 81. Motor chambers SA and SB are formed in spaces surrounded by the motor cases 11A and 11B and the partition walls 18A and 18B, and the first and second electric motors 2A and 2B are disposed in the motor chambers SA and SB, respectively. Is done. A reduction gear chamber SC as a separate chamber is formed in a space surrounded by the central case 11M and the partition walls 18A and 18B, and the first and second planetary gear type reduction gears 12A and 12B are formed in the reduction gear chamber SC. Is arranged. In other words, the partition walls 18A and 18B include a reduction gear chamber SC that houses the first and second planetary gear type reduction gears 12A and 12B, and motor chambers SA and SB that house the first and second electric motors 2A and 2B. It is partitioned.

  As shown in FIG. 2, in this embodiment, the left motor case 11A and the central case 11M constitute a first case 11L that houses the first electric motor 2A and the first planetary gear type speed reducer 12A. The right motor case 11B and the central case 11M constitute a second case 11R that houses the second electric motor 2B and the second planetary gear type speed reducer 12B. The first case 11L includes a left reservoir RL that stores oil as a liquid medium that is used for lubrication and / or cooling of at least one of the first electric motor 2A and the power transmission path, and the second case 11R includes The second electric motor 2B and the right storage part RR that stores oil used for lubrication and / or cooling of at least one of the power transmission paths are provided. The left reservoir RL and the right reservoir RR communicate with each other to form a reservoir RT. In FIG. 2, the code | symbol H has shown the oil level of the storage part RT.

  As shown in FIG. 4, the case 11 is supported by support portions 13 a and 13 b of a frame member 13 that is a part of a frame that is a skeleton of the vehicle 3 and a frame of the drive device 1 (not shown). . The support portions 13a and 13b are provided on the left and right with respect to the center of the frame member 13 in the vehicle width direction. Moreover, the arrow in FIGS. 2-5 has shown the positional relationship in the state in which the rear-wheel drive device 1 was mounted in the vehicle.

  The rear wheel drive device 1 is provided with a breather device 40 that communicates the inside and the outside of the case 11 so that the air inside is not exposed to the outside through the breather chamber 41 so that the air inside does not become excessively high temperature and pressure. Configured to escape. The breather chamber 41 is arranged in the upper part of the case 11 in the vertical direction, and includes an outer wall of the central case 11M, a first cylindrical wall 43 extending substantially horizontally in the central case 11M on the left motor case 11A side, and a right motor case. The second cylindrical wall 44 extending substantially horizontally on the 11B side, the left and right dividing walls 45 connecting the inner ends of the first and second cylindrical walls 43, 44, and the left motor case 11A of the first cylindrical wall 43 A space formed by a baffle plate 47A attached to abut on the side tip, and a baffle plate 47B attached to abut on the right motor case 11B side tip of the second cylindrical wall 44. The

  The first and second cylindrical walls 43 and 44 and the left and right dividing walls 45 forming the lower surface of the breather chamber 41 are such that the first cylindrical wall 43 is located radially inward from the second cylindrical wall 44 and the left and right dividing walls 45 are The third cylindrical wall 44 extends from the inner end portion of the second cylindrical wall 44 to the inner end portion of the first cylindrical wall 43 while being bent while being reduced in diameter, and further extends radially inward to extend substantially horizontally. The cylindrical wall 46 is reached. The third cylindrical wall 46 is located inside and substantially in the center from both outer ends of the first cylindrical wall 43 and the second cylindrical wall 44.

  In the central case 11M, baffle plates 47A and 47B are provided in the space between the first cylindrical wall 43 and the outer wall of the central case 11M or the space between the second cylindrical wall 44 and the outer wall of the central case 11M as the first planet. It is fixed so as to be separated from the gear type speed reducer 12A or the second planetary gear type speed reducer 12B.

  In addition, an external communication path 49 that connects the breather chamber 41 and the outside is connected to the central case 11M on the upper surface in the vertical direction of the breather chamber 41. The breather chamber side end portion 49a of the external communication passage 49 is arranged so as to be directed downward in the vertical direction. Accordingly, the oil is prevented from being discharged to the outside through the external communication passage 49.

  In the first and second electric motors 2A and 2B, stators 14A and 14B are fixed to motor cases 11A and 11B, respectively, and annular rotors 15A and 15B are rotatably arranged on the inner peripheral sides of the stators 14A and 14B. . Cylindrical shafts 16A and 16B surrounding the outer periphery of the axles 10A and 10B are coupled to the inner peripheral portions of the rotors 15A and 15B. The cylindrical shafts 16A and 16B (rotary shafts) can be rotated coaxially with the axles 10A and 10B. Are supported by the end walls 17A and 17B of the motor cases 11A and 11B and the partition walls 18A and 18B through first bearings 19A and 19B and third bearings 34A and 34B, respectively (see also FIG. 5). ). Further, on the outer periphery of one end side of the cylindrical shafts 16A and 16B and on the end walls 17A and 17B, the rotational position information of the rotors 15A and 15B is sent to the controller of the first and second electric motors 2A and 2B (not shown). Resolvers 20A and 20B are provided for feedback.

  The first and second electric motors 2A and 2B including the stators 14A and 14B and the rotors 15A and 15B have the same diameter, and the rotation axes of the first and second electric motors 2A and 2B are arranged on the same line X (hereinafter referred to as “the same”). , X is attached as the rotation axis X.) Also, the first and second electric motors 2A, 2B are arranged mirror-symmetrically with each other. The axle 10A and the cylindrical shaft 16A pass through the first electric motor 2A and extend from both ends of the first electric motor 2A. The axle 10B and the cylindrical shaft 16B also penetrate the second electric motor 2B. , Extending from both ends of the second electric motor 2B.

  Further, the first planetary gear type speed reducer 12A disposed on the power transmission path between the left rear wheel LWr and the first motor 2A, and the power transmission path between the right rear wheel RWr and the second motor 2B. The second planetary gear speed reducer 12B includes sun gears 21A and 21B, a plurality of planetary gears 22A and 22B meshed with the sun gears 21A and 21B, planetary carriers 23A and 23B that support the planetary gears 22A and 22B, and planetary gears. Ring gears 24A and 24B meshed with the outer peripheral sides of 22A and 22B, the driving forces of the first and second electric motors 2A and 2B are input from the sun gears 21A and 21B, and the decelerated driving force is converted to the planetary carrier 23A. It is output to the axles 10A and 10B through 23B.

  The sun gears 21A and 21B are formed integrally with the cylindrical shafts 16A and 16B. That is, the sun gears 21A and 21B of the first and second planetary gear type speed reducers 12A and 12B and the rotors 15A and 15B of the first and second electric motors 2A and 2B are mechanically connected by the cylindrical shafts 16A and 16B. Yes.

  Further, the planetary gears 22A and 22B have large-diameter first pinions 26A and 26B that are directly meshed with the sun gears 21A and 21B, and second pinions 27A and 27B that are smaller in diameter than the first pinions 26A and 26B. It is a continuous pinion. The first pinions 26A and 26B and the second pinions 27A and 27B are integrally formed in a state of being coaxial and offset in the rotation axis X direction (hereinafter referred to as the axial direction). The planetary gears 22A and 22B are supported by the pinion shafts 32A and 32B of the planetary carriers 23A and 23B via needle bearings 31A and 31B.

  The planetary carriers 23A and 23B have axially inner ends extending radially inward and are spline-fitted to the axles 10A and 10B and supported so as to be integrally rotatable, and the partition walls 18A and 18B via the second bearings 33A and 33B. It is supported by. As shown in FIG. 2, the planetary carriers 23A and 23B are partially immersed in the storage portion RT, and when the planetary carriers 23A and 23B make one round, the planetary gears 22A and 22B also enter the storage portion RT. It passes through the stored oil.

  The ring gears 24A and 24B have gear portions 28A and 28B that are meshed with the second pinions 27A and 27B whose inner peripheral surfaces are small diameters, and small diameters that are smaller than the gear portions 28A and 28B and that are opposed to each other at an intermediate position of the case 11. Parts 29A and 29B, and connecting parts 30A and 30B that connect the axially inner ends of the gear parts 28A and 28B and the axially outer ends of the small diameter parts 29A and 29B in the radial direction.

  The gear portions 28A and 28B face each other in the axial direction with a third cylindrical wall 46 formed at the inner diameter side end portion of the left and right dividing wall 45 of the central case 11M. The outer diameter surfaces of the small diameter portions 29A and 29B are spline-fitted to an inner race 51 of a one-way clutch 50, which will be described later, and the ring gears 24A and 24B are connected to each other so as to rotate integrally with the inner race 51 of the one-way clutch 50. Configured.

  On the second planetary gear type speed reducer 12B side, between the second cylindrical wall 44 of the central case 11M constituting the case 11 and the gear portion 28B of the ring gear 24B, it is connected to the ring gear 24B to constitute braking means. The hydraulic brake 60 is disposed to overlap the first pinion 26B in the radial direction and overlap the second pinion 27B in the axial direction. The hydraulic brake 60 includes a plurality of fixed plates 35 that are spline-fitted to the inner peripheral surface of the second cylindrical wall 44 and a plurality of rotary plates 36 that are spline-fitted to the outer peripheral surface of the gear portion 28B of the ring gear 24B. The plates 35 and 36 are arranged alternately in the directions, and are fastened and released by an annular piston 37. The piston 37 is accommodated in an annular cylinder chamber formed between the left and right dividing walls 45 of the central case 11M and the third cylindrical wall 46, and is provided on the outer peripheral surface of the third cylindrical wall 46. By the elastic member 39 supported by the receiving seat 38, the fixed plate 35 and the rotating plate 36 are always urged in the releasing direction.

  More specifically, the working chamber S into which oil is directly introduced is defined between the left and right dividing walls 45 and the piston 37, and when the pressure of the oil introduced into the working chamber S exceeds the urging force of the elastic member 39, The piston 37 moves forward (to the right), and the fixed plate 35 and the rotating plate 36 are pressed against each other and fastened. When the urging force of the elastic member 39 exceeds the pressure of the oil introduced into the working chamber S, the piston 37 moves backward (leftward movement), and the fixed plate 35 and the rotating plate 36 are separated and released. . The hydraulic brake 60 is connected to an electric oil pump 70 (see FIG. 4).

  In the case of this hydraulic brake 60, the fixed plate 35 is supported by the second cylindrical wall 44 extending from the left and right dividing walls 45 of the central case 11M constituting the case 11, while the rotating plate 36 is supported by the gear portion 28B of the ring gear 24B. Therefore, when the plates 35 and 36 are pressed by the piston 37, a braking force is applied to the ring gear 24B by the frictional engagement between the plates 35 and 36, and is fixed. When the fastening by the piston 37 is released from this state, the ring gear 24B is allowed to rotate freely. As described above, since the ring gears 24A and 24B are connected to each other, the braking force is also applied to the ring gear 24A when the hydraulic brake 60 is fastened, and the ring gear 24A is fixed when the hydraulic brake 60 is released. Free rotation is allowed.

  Also, a space is secured between the coupling portions 30A and 30B of the ring gears 24A and 24B facing each other in the axial direction, and only power in one direction is transmitted to the ring gears 24A and 24B in the space to transmit power in the other direction. A one-way clutch 50 is arranged to be shut off. The one-way clutch 50 has a large number of sprags 53 interposed between an inner race 51 and an outer race 52. The inner race 51 is connected to the small diameter portions 29A, 29B of the ring gears 24A, 24B by spline fitting. It is configured to rotate integrally. The outer race 52 is positioned by the third cylindrical wall 46 and is prevented from rotating.

  Next, the configuration of the partition walls 18A and 18B of this embodiment will be described in detail with reference to FIGS. The partition walls 18A and 18B are disposed outside the first and second planetary gear type speed reducers 12A and 12B in the axial direction and close to the first and second planetary gear type speed reducers 12A and 12B. Further, in the present embodiment, the partition walls 18A and 18B are made of the same member having the same origin, and the partition wall 18B is an intermediate surface M (between the partition wall 18A and the partition wall 18B perpendicular to the axial direction. 2), and is arranged so as to be mirror-symmetric with respect to the intermediate plane M. Therefore, in the following description, only one partition wall 18A is shown and described. Moreover, in FIGS. 6-9, illustration of the cylindrical shaft 16A is abbreviate | omitted. 8 to 9, the second bearing 33A is not shown.

  The partition wall 18A of the present embodiment has a surface 82 on the speed reducer chamber SC side (front side in FIG. 5) and a back surface 93 positioned opposite to the surface 82, and the first planetary gear type speed reducer 12A has The first electric motor 2 </ b> A is disposed so as to face the front surface 82 and face the back surface 93. The front surface 82 and the back surface 93 are formed so as to be inclined toward the motor chamber SA side (the back side in FIG. 5) from the radially outer side toward the rotation axis X. More specifically, the front surface 82 and the rear surface 93 of the partition wall 18A include inclined surfaces that form a conical inclined surface of a virtual cone having a vertex on the rotation axis X in a direction away from the first planetary gear speed reducer 12A. It is out. The vertex of the virtual cone constituting the inclined surface of the back surface 93 is located in a direction further away from the first planetary gear type speed reducer 12A with respect to the vertex of the virtual cone constituting the inclined surface of the surface 82, thereby The thickness of the partition wall 18A at the same circumferential position is substantially uniform from the radially inner side to the outer side.

  The front surface 82 has a smooth surface with a smooth portion other than the concave portion 84 to be described later, and the back surface 93 extends radially outward from the rotation axis X as shown in FIG. A plurality of convex ribs 94 are formed radially.

  The partition wall 18A is provided with an insertion hole through which the cylindrical shaft 16A that surrounds the outer periphery of the axle 10A is inserted on the rotation axis X. The radially inner end of the partition wall 18A (that is, the outer edge of the insertion hole) An annular projecting wall 88 projecting toward the reduction gear chamber SC in the axial direction is formed. On the outer peripheral surface of the annular projecting wall 88, a second bearing 33A that supports the first planetary gear type speed reducer 12A is disposed so as to face the surface 82. Further, the annular projecting wall 88 is partially cut away in the circumferential direction to form a gap 92, and this gap 92 is smoothly connected to a concave portion 84 described later.

  On the inner peripheral surface 89 of the insertion hole, a concave inner peripheral surface 91 that is recessed radially outward is formed at the end on the motor chamber SA side in the axial direction from the surface 82. The first bearing 19 </ b> A that supports the cylindrical shaft 16 </ b> A is disposed on the concave inner peripheral surface 91. A convex portion 90 that protrudes radially inward from the inner peripheral surface 89 is formed at the end portion on the reduction gear chamber SC side in the axial direction of the inner peripheral surface 89.

  Thus, on the annular projecting wall 88 of the partition wall 18A, the second bearing 33A that supports the planetary carrier 23A of the first planetary gear type speed reducer 12A is disposed on the radially outer side of the annular projecting wall 88, and the cylindrical shaft 16A is disposed. The supporting first bearing 19 </ b> A is disposed on the radially inner side of the annular projecting wall 88. Further, the gap portion 92 communicates the radially outer side and the radially inner side of the annular projecting wall 88.

  A part of the surface 82 has a fan-shaped concave portion 84 that is recessed radially outward from the second bearing 33 </ b> A when viewed from the axial direction and toward the motor chamber SA in the axial direction from the other portion 83. It is formed to have a predetermined length in the circumferential direction. As shown in FIG. 5B and FIG. 11, the concave portion 84 has a position where the center of the cylindrical shaft 16 </ b> A and the bolt 81 positioned on the rear side and vertically above the center of the cylindrical shaft 16 </ b> A are fastened ( Are formed substantially symmetrically on both sides in the circumferential direction with respect to a virtual line Y connecting the fastening portion). The concave portion 84 of the surface 82 is formed between two adjacent convex ribs 94 formed on the back surface 93, and the region of the back surface 93 corresponding to the concave portion 84 is between other adjacent convex portions. The convex part 95 which protruded rather than the area | region is comprised.

  As shown in FIG. 11, in an orthogonal coordinate system with the rotation axis X as the origin, the x-axis as the horizontal direction, and the y-axis as the vertical direction, the front and top are the first quadrant, the back and the top are the second quadrant, and the back When the lower quadrant is the third quadrant and the lower front is the fourth quadrant, when the planetary carrier 23A of the first planetary gear type speed reducer 12A connected to the axle 10A rotates clockwise when moving forward, the concave portion 84 Is preferably arranged to be located in the second quadrant.

  A pair of first step portions 85 a and 85 b are formed at both ends in the circumferential direction of the concave portion 84, that is, at the boundary between the concave portion 84 and the other portion 83. The pair of first step portions 85a and 85b are surfaces having a predetermined width in the axial direction, and the pair of first step portions 85a and 85b and the gap portion 92 of the annular projecting wall 88 communicate with each other. The concave portion 84 is smoothly connected to the gap portion 92 of the annular projecting wall 88. Further, in the concave portion 84, a projection 86 is formed on the imaginary line Y so as to project from the concave portion 84 toward the reduction gear chamber SC in the axial direction, and at the boundary between the projection 86 and the concave portion 84. A second stepped portion 87 is formed. Similar to the first step portions 85a and 85b, the second step portion 87 is a surface having a predetermined width in the axial direction, and the first step portions 85a and 85b and the second step portion 87 are, as will be described later. Functions as an oil guide surface. The protruding portion 86 is formed to be substantially equal to or less than the other portion 83 so that it does not protrude from the other portion 83, that is, the second stepped portion 87 is substantially equal to or less than the first stepped portions 85a and 85b. ing.

  A pair of 1st level | step-difference parts 85a and 85b and the 2nd level | step-difference part 87 are extended in the radial direction from the rotating shaft X, and have comprised the predetermined angle with respect to the horizontal direction. The pair of first step portions 85a and 85b extend from a predetermined position above the rotation axis X to the inner peripheral surface 89 of the partition wall 18A so as to go downward in the vertical direction from the radially outer side toward the rotation axis X. ing. The second stepped portion 87 extends from a predetermined position above the rotation axis X in the vertical direction to a position before the inner peripheral surface 89 of the partition wall 18A so as to go downward in the vertical direction from the radially outer side toward the cylindrical shaft 16A. ing.

  In the rear wheel drive device 1 configured as described above, while the vehicle 3 is traveling, that is, while the planetary carriers 23A and 23B connected to the axles 10A and 10B are rotating (rotating), the planetary carriers 23A and 23B are rotated and rotated. Accompanying the rotation (revolution) of the planetary gears 22A, 22B, the oil in the reservoir RT is scraped up, and a part thereof is carried to the surface 82 of the partition walls 18A, 18B. The oil transported to the concave portion 84 through the other portion 83 collides with the first step portion 85a and the second step portion 87 located above the pair of first step portions 85a and 85b in the vertical direction. 84, and is guided toward the motor chambers SA and SB in the radial direction and in the axial direction by the second stepped portion 87 and the first stepped portion 85b positioned below in the vertical direction. Lubricate 33B. Further, a part reaches the inner peripheral surface 89 of the partition walls 18 </ b> A and 18 </ b> B via the gap 92 of the annular projecting wall 88. Then, the oil falls along the inner peripheral surface 89, and the first bearings 19A and 19B disposed on the inner peripheral surface 89 are also lubricated.

  Of the oil that has been scraped up, the oil that does not reach the concave portion 84 and the oil that has passed through the concave portion 84 fall along the smooth other portion 83 and return to the reservoir portion RT.

  Returning to FIG. 2, the axle 10A is provided with a left axle oil passage 111A, and the oil supplied by the electric oil pump 70 and passing through the left axle oil passage 111A is the first planetary gear type in the speed reducer chamber SC. The needle bearing 31A of the speed reducer 12A and the meshing portions of the gears (21A, 22A, 23A, 24A) and the like are lubricated (see arrows in FIG. 2). Further, the axle 10B is provided with a right axle oil passage 111B, and the oil supplied by the electric oil pump 70 and passing through the right axle oil passage 111B is supplied to the second planetary gear reducer in the reducer chamber SC. The 12B needle bearing 31B and the meshing portions of the gears (21B, 22B, 23B, 24B) are lubricated (see the arrows in FIG. 2).

  When the vehicle 3 is stopped, that is, when there is no oil pick-up due to the rotation (rotation) of the planetary carriers 23A, 23B connected to the axles 10A, 10B and the rotation (revolution) of the planetary gears 22A, 22B. A part of the oil lubricated to each member in the speed reducer chamber SC through the left axle oil passage 111A and the right axle oil passage 111B is scattered on the surface 82 of the partition walls 18A, 18B. The oil scattered in the concave portion 84 naturally falls, and is guided toward the motor chambers SA and SB in the radial direction and in the axial direction by the second step portion 87 and the first step portion 85b positioned below the vertical direction. The second bearings 33A and 33B are lubricated. Further, a part reaches the inner peripheral surface 89 of the partition walls 18 </ b> A and 18 </ b> B via the gap 92 of the annular projecting wall 88. The oil naturally falls along the inner peripheral surface 89, and the first bearings 19A and 19B disposed on the inner peripheral surface 89 are also lubricated. The oil that does not reach the concave portion 84 naturally falls along the smooth other portion 83 and returns to the storage portion RT.

  As described above, according to the present embodiment, the partition walls 18A and 18B are formed on the part of the surface 82 facing the first and second planetary gear speed reducers 12A and 12B, on the first and second planetary gear type. The concave portion 84 is recessed in a direction away from the speed reducers 12A and 12B. The concave portion 84 is radially outer than the second bearings 33A and 33B when viewed in the axial direction, and is formed in the radial direction and the circle. Since it is formed over a region having a predetermined length in the circumferential direction, the oil is scraped up along with the rotation of the first and second planetary gear type speed reducers 12A and 12B and transmitted through the surface 82 of the partition walls 18A and 18B. Can be collected by the concave portions 84 provided in the partition walls 18A and 18B and guided radially inward to lubricate the second bearings 33A and 33B. In this way, by using the concave portion 84 provided in the partition walls 18A and 18B to guide the oil, it is possible to suppress the generation of bubbles and the generation of noise / vibration, and it is necessary as in the case of protruding from the partition walls 18A and 18B. The excessive oil collection can be prevented. Accordingly, it is possible to suppress the return of oil to the storage portion RT from being delayed.

  Further, of the surface 82, the upper boundary portion located above the concave portion 84 and the other portion 83 in the vertical direction constitutes a step-shaped first step portion 85a having a predetermined length in the axial direction. Therefore, more oil can be collected by oil colliding with the 1st level | step-difference part 85a.

  Moreover, since the partition walls 18A and 18B have protrusions 86 that protrude from the concave portion 84 in a direction close to the first and second planetary gear speed reducers 12A and 12B, more oil can be collected. Can do. Furthermore, since the first step portion 85a and the protrusion 86 extend in a direction intersecting the horizontal direction, more oil can be guided radially inward.

  Further, the protruding portion 86 is formed so that the first and second planetary gear type speed reducers 12A, 12B side end portions (top portions) of the protruding portion 86 do not protrude from the other portion 83, so that the raised oil Can be prevented from strongly hitting the protrusion 86.

  Moreover, since the other part 83 is a smooth surface formed smoothly over the area | region which has a predetermined length in the circumferential direction, it is not collected by the recessed part 84, but the excess part which passed the recessed part 84 was passed. Oil can be returned to the reservoir RT early.

  Further, the surface 82 is a virtual cone having a vertex on the rotation axis X in a direction away from the first and second planetary gear speed reducers 12A and 12B over a region having a predetermined length in the circumferential direction. Since the concave portion 84 is formed on the inclined surface including an inclined surface that forms a conical inclined surface, more oil can be guided radially inward through the concave portion 84.

  The partition walls 18A and 18B have convex ribs 94 formed on the rear surface 93 so as to extend radially outward from the rotation axis X, and the concave portion 84 has two convex shapes adjacent to each other in the circumferential direction. Since it is formed between the ribs 94, the rigidity of the partition walls 18A and 18B can be increased and vibration and noise can be suppressed. Further, since the convex rib 94 is formed not on the front surface 82 but on the rear surface 93, the return of excess oil that passes through the concave portion 84 to the storage portion RT is not hindered.

  Further, the partition walls 18A and 18B have a convex portion 95 at a position corresponding to the concave portion 84 and corresponding to the concave portion 84 on the rear surface 93. That is, the partition wall 18A, 18B has a convex portion 95 corresponding to the concave portion 84. Since the convex part 95 protrudes, the change of the thickness of the partition walls 18A and 18B with the other part 83 where the concave part 84 is not formed can be suppressed, and the local rigidity reduction and stress concentration can be suppressed. Furthermore, since the convex portion 95 is formed between the adjacent convex ribs 94, the convex rib 94 can be reinforced by the convex portion 95.

  Further, the partition walls 18A and 18B are partition walls that partition the reduction gear chamber SC and the motor chamber SA, that is, partition walls that partition the internal space, and therefore have a higher degree of design freedom than the outer wall that forms the outer shell of the case 11. Thus, the concave portion 84 that is more optimal for lubrication can be formed.

  Further, the rotor 15A of the first and second electric motors 2A and 2B is disposed on the partition walls 18A and 18B in which the second bearings 33A and 33B for rotatably supporting the first and second planetary gear type speed reducers 12A and 12B are disposed. , 15B for supporting the first and second planetary gear speed reducers 12A, 12B and the partition walls 18A, 18B can be disposed closer to each other, and the partition walls 18A, 18B can be disposed closer to each other. Can also be made thinner.

  Further, the partition walls 18A and 18B are cylinders that mechanically connect the sun gears 21A and 21B of the first and second planetary gear speed reducers 12A and 12B and the rotors 15A and 15B of the second electric motors 2A and 2B to the inside in the radial direction. The second bearings 33A and 33B are disposed on the radially outer side of the annular projecting wall 88, and the first bearings 19A and 19B are provided on the annular projecting wall 88. Arranged radially inside. Further, since the annular protruding wall 88 has a gap portion 92 that communicates the radially outer side and the radially inner side, a part of the oil that lubricates the second bearings 33A and 33B can be supplied to the first bearings 19A and 19B. .

  Moreover, since the recessed part 84 and the clearance gap 92 continue, more oil can be turned to the 1st bearing 19A, 19B.

  The planetary carriers 23A and 23B of the first and second planetary gear speed reducers 12A and 12B are mechanically connected to the rear wheel Wr of the vehicle 3, and the first and second planetary gear speed reducers 12A and 12B. When the planetary carriers 23A and 23B rotate clockwise in this orthogonal coordinate system when the vehicle 3 moves forward in an orthogonal coordinate system in which the rotation axis X is the origin, the x axis is the horizontal direction, and the y axis is the vertical direction. The concave portion 84 is formed at a position in the second quadrant. Therefore, the concave portion 84 is positioned above the rotation axis X (that is, a position that is not in the third and fourth quadrants), so that the oil collected in the concave portion 84 is naturally dropped to the second bearing 33A, To 33B. Moreover, since the distance from the oil surface to the concave portion 84 is shorter than the first quadrant, more oil can be collected in the concave portion 84.

  The partition wall 18B is disposed in such a manner that the partition wall 18A is reversely moved with respect to the intermediate surface M perpendicular to the axial direction and positioned between the partition wall 18A and the partition wall 18B and rotated with respect to the rotation axis X. , 18B can be the same member.

  Moreover, since the convex part 90 is formed in the edge part by the side of the reduction gear chamber SC in the axial direction of the internal peripheral surface 89, the oil which reached | attained on the internal peripheral surface 89 will flow into the reduction gear chamber SC side. The oil can be more easily guided to the first bearings 19A and 19B.

  In addition, this invention is not limited to embodiment mentioned above, A deformation | transformation, improvement, etc. are possible suitably.

For example, in the above embodiment, the first and second planetary gear type speed reducers 12A and 12B are exemplified as the rotating body. However, the rotating body may be a normal gear, a rotor of an electric motor, or the like.
In the above-described embodiment, the partition walls 18 </ b> A and 18 </ b> B are exemplified as the wall portion. However, the wall portion may be an outer wall constituting the housing, such as an outer wall of the case 11. The housing may be a speed reducer case that accommodates only the speed reducer, or may be a motor case that accommodates only the electric motor.
Moreover, in the said embodiment, when the planetary carriers 23A and 23B rotate clockwise in the orthogonal coordinate system shown in FIG. 11 when the vehicle 3 moves forward, the concave portion 84 is formed at a position that is in the second quadrant. However, when the planetary carriers 23A and 23B rotate counterclockwise in the orthogonal coordinate system shown in FIG. 11 when the vehicle 3 moves forward, the concave portion 84 is formed at a position that is in the first quadrant. Is preferred.
Further, in the above embodiment, the partition wall 18B shares the partition wall 18A as the same member, and is arranged in such a manner that the partition wall 18A is reversed and moved with respect to the intermediate surface M and rotated with respect to the rotation axis X. You may arrange | position in the made aspect. In this case, the recessed portion 84 of the partition wall 18A is disposed upward and rearward, and the recessed portion 84 of the partition wall 18B is disposed upward and forward. Further, the partition walls 18A and 18B are not necessarily the same member.

  In the above embodiment, the boundary between the concave portion 84 and the other portion 83 is the pair of first step portions 85a and 85b having a predetermined width in the axial direction, but when the partition walls 18A and 18B are not shared, In other words, when not composed of the same member, only the boundary located above in the vertical direction may be a stepped portion made of a surface having a predetermined width in the axial direction, and the other may be a smooth inclined surface or a curved surface.

Moreover, in the said embodiment, although the surface 82 of the partition 18A was made into the inclined surface which makes | forms the conical slope of the virtual cone which has a vertex on the rotation axis X of the direction away from the 1st planetary gear type reduction gear 12A, it is perpendicular | vertical direction. It may be a plane extending in the direction. Similarly, the back surface 93 may be a plane extending in the vertical direction. Furthermore, only the surface 82 of the partition wall 18A may be an inclined surface forming a conical slope of a virtual cone, and the back surface 93 may be a plane extending in the vertical direction.
In the above embodiment, the first stepped portions 85a and 85b and the second stepped portion 87 are provided so as to extend in the radial direction from the rotation axis X, but as long as a predetermined angle is formed with respect to the horizontal direction. , It may extend in any direction.

  Moreover, in the said embodiment, although the whole area | region of the other part 83 was made into the smooth smooth surface, about the area | region immersed in the storage part RT, a shape is not specifically limited, It can be set as arbitrary shapes.

  Moreover, in the said embodiment, although the recessed part 84 is formed to the clearance part 92 through the position which opposes the 2nd bearing 33A, the outer-diameter side edge part and / or inner-diameter side edge part of the recessed part 84 are suitably used. Can be adjusted. When the inner diameter side end portion of the concave portion 84 is positioned on the outer diameter side with respect to the position facing the second bearing 33A, separately from the inner diameter side end portion of the concave portion 84 to the position facing the second bearing 33A. What is necessary is just to form a communicating path.

3 Vehicle 11 Case (housing)
12A First planetary gear reducer (rotary body, first rotating body)
12B Second planetary gear type speed reducer (rotary body, first rotating body)
15A, 15B Rotor (Rotating body, 2nd rotating body)
16A, 16B Cylindrical shaft (connecting member)
18A Bulkhead (wall, left wall)
18B Bulkhead (wall, right wall)
19A, 19B First bearing 23A Planetary carrier (left rotating body)
23B Planetary carrier (right rotating body)
33A, 33B Second bearing 82 surface (opposing surface)
83 Other part 84 Concave part 85a 1st step part (upper boundary part)
86 Projection (convex)
88 Annular protruding wall (cylindrical part)
92 Gap part 93 Back surface 94 Convex rib (second convex part)
95 Convex part (third convex part)
M Intermediate surface SA, SB Motor chamber (second chamber)
SC Reducer room (1st room)
RT Reservoir Wr Rear wheel (wheel)
LWr Left rear wheel (left wheel)
RWr Right rear wheel (right wheel)
X axis of rotation

Claims (14)

A rotating body,
A bearing that rotatably supports the rotating body;
A wall portion in which the bearing is disposed, a storage portion for storing a lubricating fluid used for lubrication of the bearing, and a housing that houses the rotating body,
The wall portion is disposed adjacent to the rotating body on one side of the rotating body in the rotation axis direction of the rotating body,
The rotating body is arranged so that a part of the lower part in the vertical direction is immersed in the storage part,
The wall portion has a recessed portion that is recessed in a direction away from the rotating body on a facing surface facing the rotating body,
The concave portion is formed over a region having a predetermined length in the radial direction and the circumferential direction on the outer side in the radial direction than the bearing as viewed from the rotational axis direction ,
The wall portion has a second convex portion formed on the back surface opposite to the facing surface so as to extend radially outward from the rotation axis.
The lubrication structure for a bearing, wherein the concave portion is formed between two second convex portions adjacent to each other in the circumferential direction . The lubricating structure of the bearing according to claim 1,
Of the opposing surface, when the region adjacent to the concave portion in the circumferential direction and not formed with the concave portion is defined as another portion, it is located above the boundary portion of the concave portion with the other portion in the vertical direction. The upper boundary portion is a lubrication structure for a bearing, which is formed in a step shape having a predetermined length in the rotation axis direction. A lubricating structure for a bearing according to claim 2,
The upper boundary portion extends in a direction intersecting the horizontal direction, and is a lubricating structure for a bearing. The bearing lubricating structure according to any one of claims 1 to 3,
The lubrication structure for a bearing, wherein the wall portion has a convex portion projecting from the concave portion in a direction approaching the rotating body. A lubricating structure for a bearing according to claim 4,
The said convex-shaped part is a lubrication structure of a bearing extended in the direction which cross | intersects with respect to a horizontal direction. The bearing lubricating structure according to claim 4 or 5,
Of the opposing surface, when the region adjacent to the concave portion and in the circumferential direction where the concave portion is not formed is the other portion, the convex portion is the rotating body side end of the convex portion. The bearing lubrication structure is formed so as not to protrude from the part. A bearing lubricating structure according to any one of claims 1 to 6,
Of the opposing surface, when an area adjacent to the concave portion in the circumferential direction and not formed with the concave portion is defined as another portion, the other portion extends over an area having a predetermined length in the circumferential direction. A lubricating structure for a bearing having a smooth surface formed smoothly. The bearing lubricating structure according to any one of claims 1 to 7,
The facing surface includes an inclined surface forming a conical inclined surface of a virtual cone having a vertex on the rotation axis in a direction away from the rotating body over a region having a predetermined length in the circumferential direction,
The bearing has a lubricating structure formed on the inclined surface. A bearing lubrication structure according to any one of claims 1 to 8 ,
The lubricating structure for a bearing, wherein the wall portion has a third convex portion having a shape corresponding to the concave portion at a position corresponding to the concave portion on a back surface opposite to the facing surface.   A rotating body,
  A bearing that rotatably supports the rotating body;
  A wall portion in which the bearing is disposed, a storage portion for storing a lubricating fluid used for lubrication of the bearing, and a housing that houses the rotating body,
  The wall portion is disposed adjacent to the rotating body on one side of the rotating body in the rotation axis direction of the rotating body,
  The rotating body is arranged so that a part of the lower part in the vertical direction is immersed in the storage part,
  The wall portion has a recessed portion that is recessed in a direction away from the rotating body on a facing surface facing the rotating body,
  The concave portion is formed over a region having a predetermined length in the radial direction and the circumferential direction on the radially outer side than the bearing as viewed from the rotational axis direction,
  The rotating body includes a first rotating body and a second rotating body,
  The wall portion is a partition wall that partitions a first chamber that houses the first rotating body and a second chamber that houses the second rotating body,
  The first rotating body is disposed to face the facing surface,
  The second rotating body is disposed to face the back surface opposite to the facing surface in the rotation axis direction, and is rotatably supported by the partition wall by another bearing different from the bearing,
  The partition wall has a cylindrical portion extending in the rotational axis direction through a connecting member that mechanically connects the first rotating body and the second rotating body on a radially inner side,
  The bearing is disposed on the radially outer side of the cylindrical portion, and the other bearing is disposed on the radially inner side of the cylindrical portion,
  The lubricating structure of the bearing, wherein the cylindrical portion includes a communication path that communicates the radially outer side and the radially inner side. The bearing lubricating structure according to claim 10 ,
A lubrication structure for a bearing in which the concave portion and the communication path are continuous. A lubricating structure for a bearing according to claim 10 or 11 ,
The first rotating body is one of a rotor of an electric motor and a transmission mechanically connected to the rotor,
The second rotating body is a lubricating structure of a bearing, which is the other of the rotor and the transmission. The bearing lubricating structure according to any one of claims 1 to 12 ,
The rotating body is mechanically connected to a vehicle wheel,
An orthogonal coordinate system in which the rotation axis of the rotating body is the origin, the x-axis is the horizontal direction, and the y-axis is the vertical direction.
When the rotating body rotates clockwise in the orthogonal coordinate system when the vehicle moves forward, the concave portion is formed at a position that becomes the second quadrant,
A bearing lubrication structure in which the concave portion is formed at a position in the first quadrant when the rotating body rotates counterclockwise in the orthogonal coordinate system when the vehicle moves forward. A lubrication structure for bearing according to any one of claims 1 to 13
The rotating body includes a left rotating body mechanically connected to a left wheel of a vehicle, and a right rotating body mechanically connected to a right wheel of the vehicle,
The wall portion includes a left wall portion disposed close to the left rotator, and a right wall portion disposed close to the right rotator,
The right wall portion is an aspect in which the left wall portion is reversed and moved relative to an intermediate surface that is orthogonal to the rotation axis direction and is located between the left wall portion and the right wall portion, or with respect to the intermediate surface A lubricating structure for a bearing, wherein the lubricating structure is disposed in a manner in which the left wall portion is reversed and moved with respect to the rotation axis.

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