Classifications

• • H—ELECTRICITY
  • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
  • H02K—DYNAMO-ELECTRIC MACHINES
  • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
  • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
  • H02K7/116—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H57/00—General details of gearing
  • F16H57/04—Features relating to lubrication or cooling or heating
• • H—ELECTRICITY
  • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
  • H02K—DYNAMO-ELECTRIC MACHINES
  • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
  • H02K7/006—Structural association of a motor or generator with the drive train of a motor vehicle
• • H—ELECTRICITY
  • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
  • H02K—DYNAMO-ELECTRIC MACHINES
  • H02K9/00—Arrangements for cooling or ventilating
  • H02K9/19—Arrangements for cooling or ventilating for machines with closed casing and closed-circuit cooling using a liquid cooling medium, e.g. oil

Definitions

• This disclosure relates to a vehicle drive system.
• a technique is known in which a groove is provided on the inner circumferential surface of the bearing hole into which the rolling bearing fits, connecting the housing chamber in the case with the internal space of the bearing hole.
• the peripheral wall portion that forms the bearing fitting hole has a groove portion of a fixed shape formed over its entire axial length, so there is a risk that the desired oil flow will not be achieved if the vehicle's position in the axial direction changes.
• the present disclosure aims to reduce or eliminate the shortage of oil supply to the bearings even when the vehicle's attitude changes in the axial direction.
• a power transmission mechanism including a rotating shaft member capable of transmitting power from a power source to a wheel; a bearing that rotatably supports the rotating shaft member; a case that houses a power transmission mechanism in a housing chamber through which oil flows and has a bearing support portion that fixedly supports the bearing; An oil passage structure at least a part of which is formed in the case,
• the bearing support portion is a first wall portion formed around the shaft and radially facing the bearing; a second wall portion formed around the shaft and facing an outer circumferential portion of the bearing from a first axial side
• the oil passage structure includes a first groove portion formed in the first wall portion so as to be recessed radially outward, The first groove portion has a first guide surface facing obliquely downward,
• a vehicle drive device is provided, wherein the first guide surface extends axially and downwardly from an end portion on a second axial side of the first wall portion toward an end portion on a first axial side.
• the present disclosure makes it possible to reduce or eliminate a shortage of oil supply to the bearings even when the vehicle's position changes in the axial direction.
• FIG. 1 is a schematic top view showing a state in which a vehicle drive device is mounted in a vehicle.
• 2 is a schematic cross-sectional view of a main portion of a vehicle drive device.
• FIG. FIG. 1 is a skeleton diagram showing a vehicle drive device.
• 3 is a diagram illustrating an oil flow in the vehicle drive device according to the present embodiment.
• FIG. 4 is a plan view showing a schematic view of a portion of the motor case as viewed from a second axial side A2.
• FIG. 4 is a perspective view showing a schematic view of a part of the motor case as viewed from a second axial side A2.
• FIG. 5 is an explanatory diagram showing an enlarged view of a part of FIG. 4 .
• 4 is a cross-sectional view showing the state of the oil passage structure when the vehicle is tilted.
• the directions of each component in the following description refer to the directions when the component is assembled into the vehicle drive device 100. Furthermore, the terms used for the dimensions, orientation, and position of each component are concepts that include differences due to errors (errors that are acceptable in manufacturing).
• driving connection refers to a state in which two rotating elements are connected so as to be able to transmit a driving force (synonymous with torque), and includes a state in which the two rotating elements are connected so as to rotate as a unit, or a state in which the two rotating elements are connected so as to be able to transmit a driving force via one or more transmission members.
• Such transmission members include various members (e.g., shafts, gear mechanisms, belts, chains, etc.) that transmit rotation at the same speed or at a variable speed.
• the transmission members may also include engagement devices (e.g., friction engagement devices, meshing engagement devices, etc.) that selectively transmit rotation and driving force.
• rotating electric machine is used as a concept that includes motors, generators, and motor/generators that function as both a motor and a generator as necessary.
• overlapping when viewed in a specific direction means that when an imaginary line parallel to the line of sight is moved in each direction perpendicular to the imaginary line, there is at least a part of an area where the imaginary line intersects with both of the two components.
• arrangement areas in a specific direction overlap means that at least a part of the arrangement area of the other component in a specific direction is included within the arrangement area of one component in a specific direction.
• FIG. 1 is a schematic diagram of a top view showing the state in which the vehicle drive device 100 is mounted in the vehicle VC.
• FIG. 2 is a cross-sectional view of a main part of the vehicle drive device 100.
• FIG. 2A is a skeleton diagram showing the vehicle drive device 100.
• FIG. 2B is a diagram showing the flow of oil in the vehicle drive device 100 according to this embodiment. In FIG. 2B, the oil that accumulates in the lower part of the case 2 (the lower part of the storage chamber SP) is shown typically by a hatched area, and the flow of oil is shown typically by arrows R20, etc.
• FIG. 3 is a plan view showing a schematic view of a part of the motor case 250 as viewed from the second axial side A2.
• FIG. 3 is a plan view showing a schematic view of a part of the motor case 250 as viewed from the second axial side A2.
• FIG. 4 is a perspective view showing a schematic view of a part of the motor case 250 as viewed from the second axial side A2.
• FIG. 5 is an explanatory diagram showing an enlarged part of FIG. 4. Note that in FIG. 4 and FIG. 5, etc., the illustration of the bearing 243, etc. is omitted. In FIG. 5, the flow of oil is shown typically by arrows R5, R6, etc.
• Figure 6 is a cross-sectional view showing the state of the oil passage structure when the vehicle is tilted.
• Figure 6 is a cross-sectional view of the motor case 250 taken along a plane including both the axial direction A and the second direction Y.
• the third defines a first direction X and a second direction Y.
• the first direction X, the second direction Y, and the axial direction A are three axial directions that are mutually perpendicular, and the second direction Y has an up-down component.
• the second direction Y may be parallel to the direction of gravity (vertical direction) or inclined when the vehicle driving device 100 is mounted on the vehicle VC.
• the vehicle driving device 100 may be mounted on the vehicle VC with the second direction first side Y1 on the upper side and the second direction second side Y2 on the lower side.
• the vehicle driving device 100 may also be mounted on the vehicle VC with the first direction first side X1 on the front side (front side in the vehicle longitudinal direction) and the first direction second side X2 on the rear side (rear side in the vehicle longitudinal direction). As shown in FIG. 1, the vehicle drive device 100 may be mounted forward of the center of the vehicle VC in the vehicle's fore-and-aft direction, or may be mounted rearward of the center of the vehicle VC in the vehicle's fore-and-aft direction. When the vehicle drive device 100 is mounted rearward of the center of the vehicle VC in the vehicle's fore-and-aft direction in this manner, the pair of wheels W driven by the vehicle drive device 100 may be, for example, a pair of left and right rear wheels.
• the pair of left and right front wheels and the pair of left and right rear wheels that are not driven by the vehicle drive device 100 can be configured to be driven by a drive device other than the vehicle drive device 100.
• the drive device other than the vehicle drive device 100 can be, for example, a drive device configured to transmit the output torque of an internal combustion engine to a pair of wheels to be driven, a drive device configured to transmit the output torque of a rotating electric machine (a rotating electric machine other than the rotating electric machine 1 provided in the vehicle drive device 100) to a pair of wheels to be driven, or a drive device configured to transmit the output torque of both an internal combustion engine and a rotating electric machine (a rotating electric machine other than the rotating electric machine 1 provided in the vehicle drive device 100) to a pair of wheels to be driven.
• the drive device other than the vehicle drive device 100 can also be a drive device with the same configuration as the vehicle drive device 100.
• the vehicle drive device 100 includes a rotating electric machine 1, a pair of output members 6 that are drivingly connected to a pair of wheels W (see Fig. 1), and a transmission mechanism 3 that transmits driving force between the rotating electric machine 1 and the pair of output members 6.
• the vehicle drive device 100 further includes a case 2 that houses the rotating electric machine 1.
• the case 2 also houses the pair of output members 6 and the transmission mechanism 3.
• the first output member 61 which is one of the pair of output members 6, is drivingly connected to the first wheel W1, which is one of the pair of wheels W
• the second output member 62 which is the other of the pair of output members 6, is drivingly connected to the second wheel W2, which is the other of the pair of wheels W.
• the vehicle VC on which the vehicle drive device 100 is mounted includes a first drive shaft 63 that rotates integrally with the first wheel W1 and a second drive shaft 64 that rotates integrally with the second wheel W2.
• the first drive shaft 63 is connected to the first wheel W1 via, for example, a constant velocity joint
• the second drive shaft 64 is connected to the second wheel W2 via, for example, a constant velocity joint.
• the first output member 61 is connected to the first drive shaft 63 so as to rotate integrally with the first drive shaft 63
• the second output member 62 is connected to the second drive shaft 64 so as to rotate integrally with the second drive shaft 64.
• the vehicle drive device 100 transmits the output torque of the rotating electric machine 1 to a pair of wheels W via a pair of output members 6 to drive the vehicle VC on which the vehicle drive device 100 is mounted. That is, the rotating electric machine 1 is a driving force source for the pair of wheels W.
• the pair of wheels W is a pair of left and right wheels (e.g., a pair of left and right front wheels, or a pair of left and right rear wheels) on the vehicle VC.
• the rotating electric machine 1 may be, for example, an AC rotating electric machine driven by three-phase AC.
• the rotating electric machine 1 is electrically connected to a battery BA (including a storage device such as a capacitor) via an inverter device (not shown) that converts power between DC power and AC power, and receives power from the battery BA to drive the vehicle, or supplies power generated by the inertial force of the vehicle VC to the storage device for storage.
• a battery BA including a storage device such as a capacitor
• an inverter device not shown
• the rotating electric machine 1 and the pair of output members 6 are arranged on two parallel axes (specifically, a first axis C1 and a second axis C2). Specifically, the rotating electric machine 1 is arranged on the first axis C1, and the pair of output members 6 are arranged on a second axis C2 different from the first axis C1.
• the first axis C1 and the second axis C2 are axes (virtual axes) arranged parallel to each other.
• the transmission mechanism 3 includes an output gear (ring gear) 30 that is drivingly connected to at least one of the pair of output members 6, and is coaxial with the pair of output members 6 (i.e., on the second axis C2).
• the vehicle drive device 100 is mounted on the vehicle VC with the axial direction A oriented along the vehicle left-right direction.
• the axial direction A is parallel to the first axis C1 and the second axis C2, in other words, the axial direction is common between the first axis C1 and the second axis C2. That is, the axial direction A is the direction in which the rotation axis of the rotating electric machine 1 extends, and is also the direction in which the rotation axis of the pair of output members 6 extends.
• one side of the axial direction A is the axial first side A1
• the other side of the axial direction A (the side opposite to the axial first side A1 in the axial direction A) is the axial second side A2.
• the axial first side A1 is the side on which the rotating electric machine 1 is disposed relative to the transmission mechanism 3 in the axial direction A.
• the first output member 61 is the output member 6 disposed on the axial first side A1 of the pair of output members 6, and the second output member 62 is the output member 6 disposed on the axial second side A2 of the pair of output members 6.
• the vehicle drive device 100 may be mounted on the vehicle VC with the first axial side A1 facing the left side of the vehicle and the second axial side A2 facing the right side of the vehicle.
• the first wheel W1 to which the first output member 61 is drivingly connected is the left wheel
• the second wheel W2 to which the second output member 62 is drivingly connected is the right wheel.
• FIG. 1 assumes that the vehicle drive device 100 is a front-wheel drive type drive device that drives a pair of left and right front wheels. Therefore, in the example shown in FIG. 1, the first wheel W1 is the left front wheel, and the second wheel W2 is the right front wheel.
• the rotating electric machine 1 includes a rotor 10 and a stator 11.
• the stator 11 is fixed to a case 2, and the rotor 10 is supported by the case 2 so as to be rotatable relative to the stator 11.
• the rotating electric machine 1 may be an inner rotor type rotating electric machine, in which case the rotor 10 may be arranged radially inside the stator 11 so as to overlap with the stator 11 when viewed radially along the radial direction.
• the radial direction here is the radial direction based on the first axis C1, in other words, the radial direction based on the rotation axis of the rotating electric machine 1.
• the stator 11 includes a stator core 12 and coil end portions 13 that protrude from the stator core 12 in the axial direction A.
• a coil is wound around the stator core 12, and the portion of the coil that protrudes from the stator core 12 in the axial direction A forms the coil end portions 13.
• the coil end portions 13 are formed on both sides of the stator core 12 in the axial direction A.
• the transmission mechanism 3 includes a counter gear mechanism 4 in the power transmission path between the rotating electric machine 1 and the output gear 30.
• a reduction mechanism using planetary gears may be used instead of the counter gear mechanism 4.
• a two-shaft configuration may be realized in which the third shaft C3 is eliminated.
• the counter gear mechanism 4 is disposed on an axis (i.e., the third axis C3) offset from the input member 16 coaxial with the rotating electric machine 1.
• the input member 16 is connected to the rotor 10 so as to rotate integrally with the rotor 10.
• the vehicle drive device 100 includes a rotor shaft 15 to which the rotor 10 is fixed, and the input member 16 is connected to the rotor shaft 15 so as to rotate integrally with the rotor shaft 15.
• the first axial side A1 of the input member 16 may be connected (here, spline connected) to the second axial side A2 of the rotor shaft 15.
• the rotor shaft 15 of the vehicle drive device 100 may be configured to be integrally formed with the input member 16 as one piece.
• the rotor shaft 15 is hollow and has an axial oil passage 15a, but may be solid.
• the counter gear mechanism 4 has a counter shaft 41, a first counter gear 42, and a second counter gear 43.
• the counter shaft 41 is a rotating shaft member that rotates around the third axis C3.
• the third axis C3 extends parallel to the first axis C1.
• the first counter gear 42 is an input element of the counter gear mechanism 4.
• the first counter gear 42 meshes with the input gear 17 of the input member 16.
• the first counter gear 42 is connected to the counter shaft 41 so as to rotate integrally with the counter shaft 41.
• the second counter gear 43 is an output element of the counter gear mechanism 4.
• the second counter gear 43 is formed with a smaller diameter than the first counter gear 42.
• the second counter gear 43 is provided on the counter shaft 41 so as to rotate integrally with the counter shaft 41.
• the differential gear mechanism 5 is disposed on the second axis C2, which serves as the rotation axis of the differential gear mechanism 5.
• the differential gear mechanism 5 distributes the driving force transmitted from the rotating electric machine 1 to the pair of output members 6.
• the differential gear mechanism 5 may be disposed coaxially with the pair of output members 6 (i.e., on the second axis C2).
• the differential gear mechanism 5 distributes the driving force transmitted from the rotating electric machine 1 to the output gear 30 to the pair of output members 6.
• the output gear 30 is drivingly connected to both of the pair of output members 6 via the differential gear mechanism 5.
• the differential gear mechanism 5 may be a bevel gear type differential gear mechanism, and the output gear 30 may be connected to the differential case portion 50 of the differential gear mechanism 5 so as to rotate integrally with the differential case portion 50.
• Case 2 may be made of aluminum, for example. Case 2 can be formed by casting, etc. Case 2 includes a motor case 250, a cover member 252, and a gear case member 254.
• the motor case 250 forms a motor housing chamber SP1 that houses the rotating electric machine 1.
• the motor housing chamber SP1 may be an oil-tight space that contains oil for cooling and/or lubricating the rotating electric machine 1 (and/or the transmission mechanism 3).
• the motor case 250 has a peripheral wall that surrounds the radial outside of the rotating electric machine 1.
• the motor case 250 may be realized by joining multiple members.
• the motor case 250 has a partition wall portion 26 that separates the motor housing chamber SP1 and the gear housing chamber SP2 in the axial direction A.
• the partition wall portion 26 faces the bottom portion 2521 (described later) of the cover member 252 in the axial direction A.
• the second axial side A2 of the partition wall 26 is provided with a connecting portion 2502 for connecting with the gear case member 254, a bearing support portion 2504 for supporting the bearing 241, and the like.
• the second axial side A2 of the partition wall 26 is also provided with a bearing support portion 2534 for supporting the bearing 243.
• the bearing support portion 2534 is formed concentrically around the third axis C3.
• the bearing 243 is provided radially outward at the end of the first axial side A1 of the countershaft 41.
• the bearing 243 is supported by the bearing support portion 2534 at the radially outward side of the outer race, and the inner radial side of the inner race is supported by the outer peripheral surface of the countershaft 41.
• the cover member 252 is connected to the first axial side A1 of the motor case 250.
• the cover member 252 is in the form of a cover that covers the first axial side A1 of the motor housing chamber SP1.
• the cover member 252 may cover the opening of the first axial side A1 of the motor case 250 in such a manner that it completely or almost completely blocks the opening. Note that a portion of the first axial side A1 of the motor housing chamber SP1 may be formed by the cover member 252.
• the cover member 252 is provided with a bearing 240 that rotatably supports the rotor 10. That is, the cover member 252 has a bearing support portion 2524 that supports the bearing 240.
• the bearing 240 is provided on the radially inner side of the end of the rotor shaft 15 on the first axial side A1, as shown in FIG. 2. Specifically, the bearing 240 has the radially outer side of the outer race supported by the inner circumferential surface of the rotor shaft 15, and the radially inner side of the inner race supported by the cover member 252.
• the bearing 241 is provided on the radially outer side of the end of the rotor shaft 15 on the second axial side A2, as shown in FIG. 2. Specifically, the bearing 241 has the radially outer side of the outer race supported by the partition wall portion 26, and the radially inner side of the inner race supported by the outer circumferential surface of the rotor shaft 15.
• the bearing 240 may be supplied with oil by a natural lubrication method, as shown in FIG. 2B.
• R21, R22, R23, and 2650 represent the flow of oil that guides the oil to the bearing 240 and its oil path.
• the cover member 252 includes a circular bottom 2521 centered on the first axis C1 and a peripheral wall 2522 protruding from the outer periphery of the bottom 2521 toward the second axial side A2, and the end face of the second axial side A2 of the peripheral wall 2522 is connected to the motor case 250.
• a cylindrical bearing support portion 2524 protruding toward the second axial side A2 is formed in the center of the second axial side A2 of the bottom 2521 (the portion centered on the first axis C1).
• the gear case member 254 forms a gear housing chamber SP2 that houses the transmission mechanism 3.
• the gear housing chamber SP2 may be an oil-tight space that communicates with the motor housing chamber SP1.
• the gear case member 254 is coupled to the second axial side A2 of the motor case 250.
• the gear case member 254 is coupled to the motor case 250 in such a manner that the mating surface 2548 abuts against the corresponding mating surface 2508 of the motor case 250 in the axial direction A at the coupling portion 2502.
• the gear case member 254 has a peripheral wall portion 2542 that surrounds the radial outside of the transmission mechanism 3, and is in the form of a cover that covers the second axial side A2 of the gear housing chamber SP2.
• the gear case member 254 may be realized by coupling multiple members. A part of the first axial side A1 of the gear housing chamber SP2 may be formed by the motor case 250.
• the gear case member 254 is provided with a bearing support 2574 that rotatably supports the counter shaft 41 via a bearing 247, as well as other similar bearing support parts.
• housing chamber SP the oil passage structure in this embodiment will be described with reference to FIG. 2B and FIG. 3 onwards.
• housing chamber SP when there is no particular distinction between the motor housing chamber SP1 and the gear housing chamber SP2 described above, they will simply be referred to as housing chamber SP.
• oil is circulated within the vehicle drive device 100 not by a so-called forced lubrication method that uses only an oil pump (mechanical or electric oil pump 82), but by combining it with a lubrication method (natural lubrication method) that lubricates the oil by scooping it up with the rotation of the gears.
• a so-called forced lubrication method that uses only an oil pump (mechanical or electric oil pump 82)
• a lubrication method naturally lubrication method
• only the forced lubrication method may be implemented.
• the oil that accumulates in the lower part of the accommodation chamber SP is scooped up by the rotation of the output gear 30 (so-called diff ring) of the differential gear mechanism 5 (see arrow R20 in FIG. 2B) and is supplied to various objects to be lubricated.
• the oil in the accommodation chamber SP may also be scooped up by a rotating body other than the output gear 30 (for example, other gears or fins).
• the gear housing SP2 may be provided with a catch tank 920 as shown in FIG. 2B.
• Oil from the catch tank 920 may be supplied to various objects to be cooled/lubricated (see arrow R21 in FIG. 2B, etc.).
• the oil in the gear housing SP2 is pumped up by a mechanical or electric oil pump 82 through a strainer 80 and an oil passage 81 (arrow R300), and is cooled through an oil cooler 90 that may be provided in the gear case member 254 (arrows R302, R303, R304, etc.).
• 84 and 86 are schematic oil passages to the oil cooler 90, and the arrow R200 represents the flow of cooling water.
• Oil from the mechanical or electric oil pump 82 may be supplied to the axial oil passage 15a of the rotor shaft 15 and the coil end portion 13 through the oil passage 86 (see arrows R306 and R307).
• the partition portion 26 is formed with an oil passage structure 70 related to the supply of oil to the bearing 243 at the bearing support portion 2534 and its periphery.
• the gear case member 254 is formed with an oil passage structure (not shown) related to the supply of oil to the bearing 247 at the bearing support portion 2574 and its periphery.
• the oil passage structure related to the supply of oil to the bearing 247 may be substantially similar to the oil passage structure 70 described below, and a detailed description thereof will be omitted.
• the oil passage structure 70 includes a first groove portion 71, a second groove portion 72, and a third groove portion 73.
• the radial direction and the circumferential direction are defined as directions based on the third axis C3.
• the first groove portion 71 is formed in the peripheral wall portion 25340 of the bearing support portion 2534 in a manner that is recessed radially outward.
• the peripheral wall portion 25340 of the bearing support portion 2534 extends around the third axis C3 and in the axial direction A (protruding further radially outward than the peripheral portion) and is a portion that faces the bearing 243 in the radial direction.
• the peripheral wall portion 25340 may abut radially from the radial outside against the outer peripheral surface of the outer race of the bearing 243.
• the first groove portion 71 has a first guide surface 710 that faces diagonally downward (second side Y2 in the second direction).
• the first guide surface 710 is formed on the side surface of the first groove portion 71 when viewed in the concave depth direction of the first groove portion 71. Note that "facing diagonally downward” is a concept that includes a state in which the normal direction of the first guide surface 710 does not coincide with the vertical direction, but the normal direction of the first guide surface 710 has a vertical component. The same applies to the second guide surface 720 described below.
• the first guide surface 710 of the first groove portion 71 extends downward in the axial direction A from the end of the peripheral wall portion 25340 on the second axial side A2 toward the end of the first axial side A1.
• the first guide surface 710 does not need to be flat all over, and may include steps or curved surfaces.
• the first guide surface 710 has the function of supplying oil to the second guide surface 720 (described below) when the vehicle tilts in the left-right direction.
• the first guide surface 710 of the first groove portion 71 extends in a direction inclined by a first angle ⁇ 1 with respect to the horizontal plane.
• the magnitude of the first angle ⁇ 1 is significantly greater than 0.
• the vehicle drive device 100 inclines in the left-right direction of the vehicle due to a change in the attitude of the vehicle in the left-right direction of the vehicle.
• the first angle ⁇ 1 may be set according to the range of possible inclination angles when the vehicle drive device 100 inclines in this manner.
• the vehicle drive device 100 and the case 2 associated therewith are inclined at an angle ⁇ (>0) with respect to the horizontal plane HL, with the second axial side A2 located lower than the first axial side A1.
• the angle ⁇ of the first guide surface 710 with respect to the horizontal plane HL is still significantly greater than 0. This allows the oil to be guided to the second groove portion 72 via the first guide surface 710 even when the vehicle is tilted in the left-right direction (see arrow R6 in FIG. 6).
• the amount of oil that flows along the first guide surface 710 to the first axial side A1 (see arrow R6 in FIG. 5), that is, the amount of oil that flows to the back side of the bearing 243, can be efficiently increased among the oil that reaches the end of the second axial side A2 of the first groove portion 71.
• the inclination (inclination of the first guide surface 710) with respect to the horizontal plane HL increases for the oil passage structure 70 on the bearing 243 side, and oil is supplied to the back side of the bearing 243 without any problems.
• the oil passage structure corresponding to the oil passage structure 70 on the bearing support portion 2574 side functions in the same way, and the oil flowing to the back side of the bearing 247 can be efficiently increased.
• the first angle ⁇ 1 may be set to a value equal to or greater than ⁇ Max. In this case, it is possible to increase the possibility of ensuring that oil can flow along the first guide surface 710 to the first axial side A1, regardless of the vehicle posture.
• the first groove portion 71 has a groove width (the distance between the first guide surface 710 and the surface facing it) that gradually decreases from the end of the second axial side A2 toward the end of the first axial side A1 from the viewpoint of manufacturability.
• the other side surface of the first groove portion 71 that faces the first guide surface 710 may be inclined in the same direction as the first guide surface 710, or in the opposite direction, at an angle significantly smaller than the first angle ⁇ 1.
• the second groove portion 72 is formed in the outer periphery 253420 of the bottom wall portion 25342 of the bearing support portion 2534 in a manner that is recessed toward the first axial side A1.
• the outer periphery 253420 of the bottom wall portion 25342 of the bearing support portion 2534 extends around the third axis C3 in the axial direction A and is a portion that faces the bearing 243 in the axial direction A.
• the outer periphery 253420 of the bottom wall portion 25342 of the bearing support portion 2534 may abut against the end face of the first axial side A1 of the outer race of the bearing 243 in the axial direction A from the first axial side A1.
• the second groove portion 72 has a second guide surface 720 that faces diagonally downward (second side Y2 in the second direction).
• the second guide surface 720 is formed on the side surface of the second groove portion 72 when viewed in the concave depth direction of the second groove portion 72.
• the second guide surface 720 of the second groove portion 72 extends radially and downward from the radially outer end of the outer periphery 253420 to the radially inner end.
• the second guide surface 720 does not need to be flat over its entirety, and may include steps or curved surfaces.
• the second guide surface 720 has the function of supplying oil to the bottom wall portion 25342 when the vehicle is tilted in the fore-and-aft direction.
• the second guide surface 720 of the second groove portion 72 extends in a direction inclined by a second angle ⁇ 2 with respect to the horizontal plane.
• the magnitude of the second angle ⁇ 2 is significantly greater than 0.
• the vehicle drive device 100 inclines in the vehicle longitudinal direction due to a change in the attitude of the vehicle in the vehicle longitudinal direction.
• the second angle ⁇ 2 may be set to a value equal to or greater than the maximum value of the range of possible inclination angles when the vehicle drive device 100 inclines.
• the oil can be guided to the back side (first axial side A1) of the bearing 243 via the second guide surface 720 even when the vehicle inclines in the longitudinal direction, based on the same principle as that described above with reference to FIG. 6.
• the oil that flows radially inward along the second guide surface 720 that is, the oil that flows to the back side of the bearing 243, can be efficiently increased among the oil that reaches the radially outer end of the second groove portion 72.
• the second groove portion 72 has a groove width (the distance between the second guide surface 720 and the surface facing it) that is substantially constant.
• the distance between the second guide surface 720 and the surface facing it may increase or decrease as it moves radially inward.
• the second guide surface 720 of the second groove portion 72 may terminate radially inward at a height position (position in the second direction Y) that is approximately the same as the third axis C3.
• the first guide surface 710 can extend to a position higher than the third axis C3 over almost the entire length. This allows oil to be efficiently supplied to a relatively wide area on the back side of the bearing 243 via the first guide surface 710 and the second guide surface 720.
• the third groove portion 73 is formed in the axial end surface 253402 of the second axial side A2 of the peripheral wall portion 25340 in a manner that is recessed toward the first axial side A1.
• the depth (axial dimension) of the third groove portion 73 may correspond to the protruding height of the peripheral wall portion 25340 (the protruding height in the axial direction relative to the radially outer peripheral portion).
• the third groove portion 73 has a radially inner end connected to an end of the first groove portion 71 on the second axial side A2.
• the third groove portion 73 extends over a circumferential section above the third axis C3, and is connected to the first groove portion 71 at its lower circumferential end.
• the depth (dimension in the axial direction A) of the third groove portion 73 may be significantly shorter than the extension range of the first groove portion 71 in the axial direction A.
• the third groove portion 73 has the function of guiding the oil that flows down from above it under its own weight (see arrow R25 on the left side of FIG. 2B) to the inlet of the first groove portion 71 (i.e., the end of the first groove portion 71 on the second axial side A2). This makes it possible to efficiently increase the amount of oil that flows to the inlet of the first groove portion 71 (see arrow R5 in FIG. 5) out of the oil that flows down from the upper side of the third groove portion 73 under its own weight. As a result, oil can be efficiently supplied to the back side of the bearing 243.
• the third groove portion 73 may be positioned with respect to the catch tank 920 so as to receive a relatively large amount of oil from the catch tank 920.
• first groove portion 71 and the second groove portion 72 formed in the peripheral wall portion 25340 of the bearing support portion 2534 are formed circumferentially offset from the third groove portion 73 also formed in the peripheral wall portion 25340. This is advantageous in terms of the strength of the peripheral wall portion 25340 of the bearing support portion 2534 compared to a case in which these three groove portions are formed in the same circumferential range.
• the depth (radial dimension) of the first groove portion 71 is significantly smaller than the radial dimension of the peripheral wall portion 25340 of the bearing support portion 2534. This makes it easier to ensure the necessary strength of the peripheral wall portion 25340 of the bearing support portion 2534 than when the depth (radial dimension) of the first groove portion 71 is the same as the radial dimension of the peripheral wall portion 25340.
• the depth (dimension in the axial direction A) of the third groove portion 73 is significantly smaller than the dimension in the axial direction A of the peripheral wall portion 25340 of the bearing support portion 2534 (the dimension in the axial direction A from the axial end face 253402 to the outer periphery 253420 or the bottom wall portion 25342). This makes it easier to ensure the necessary strength of the peripheral wall portion 25340 of the bearing support portion 2534 than when the depth (dimension in the axial direction A) of the third groove portion 73 is the same as the dimension in the axial direction A of the peripheral wall portion 25340.
• this embodiment can reduce or eliminate the shortage of oil supplied to the bearing 243 that may occur due to the vehicle's posture while ensuring the necessary strength of the bearing support portion 2534.
• the oil passage structure 70 is applied to the bearing support portion 2534 of the countershaft 41, but it may also be applied to other bearing support portions.
• 100 Vehicle drive device, 1: Rotating electric machine (power source), 2: Case, 4: Counter gear mechanism (power transmission mechanism), 243: Bearing, 2534: Bearing support portion, 25340: Peripheral wall portion (first wall portion), 253402: Axial end surface, 25342: Bottom wall portion (second wall portion), 253420: Outer periphery, 70: Oil passage structure, 71: First groove portion, 710: First guide surface, 72: Second groove portion, 720: Second guide surface, 73: Third groove portion

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• General Details Of Gearings (AREA)

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• 2024
  • 2024-02-05 EP EP24778680.9A patent/EP4692600A1/en active Pending
  • 2024-02-05 CN CN202480022922.4A patent/CN120898091A/zh active Pending
  • 2024-02-05 WO PCT/JP2024/003641 patent/WO2024202535A1/ja not_active Ceased
  • 2024-02-05 JP JP2025509833A patent/JPWO2024202535A1/ja active Pending

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