FR3091737A1 - Lubrication structure of a hybrid vehicle drive device - Google Patents

Abstract

In a driving device (4), an input shaft (34), a first and second shafts (35, 36) are provided separated from each other in an up-down direction so that a speed reduction mechanism (33 ) or projecting upwards relative to a speed change mechanism (11). A transmission housing (5) includes an oil trough (66) scraped by a pinion and supplying lubricating oil to the gear change mechanism (11). The oil gutter (66) is provided at a lower part of the speed reducer mechanism (33) to catch lubricating oil scattered from the speed reducer mechanism (33) and flowing down and provides oil to a circulation space of a bearing holding part (51A, 51B, 51D, 51E, 51F) supporting the second intermediate shaft (36). Abstract Figure: Figure 4

Description

Lubrication structure of a hybrid vehicle drive device

The present disclosure relates to the field of a lubricating structure of a hybrid vehicle drive device.

A transmission in which an oil trough is provided in a transmission housing housing an input shaft or a countershaft constituting a gear change mechanism is known as a vehicle-mounted transmission (see Patent Document 1: JP 2011-137493 A). Lubricating oil is stored in a bottom portion of the transmission case and the oil trough captures oil scraped by a final driven gear of a differential device and guides the oil to a lubricating target portion such a synchronization mechanism or a bearing provided at an end portion of an input shaft or a countershaft.

In such a conventional transmission, since the lubricating oil scraped by the final driven gear is captured by the oil trough, the amount of lubricating oil flowing into the oil trough is limited. Therefore, it is feared that a sufficient amount of the lubricating oil cannot be supplied to the bearing or the synchronization mechanism.

For example, when a speed reduction mechanism is provided as the lubricating target part other than the synchronization mechanism or the bearing provided in the input shaft or the output shaft, a sufficient amount of the lubricating oil cannot be supplied only by the lubricating oil entering the oil trough. Therefore, it is feared that the lubricating performance of the shift mechanism or the gear reducer mechanism will be degraded.

This invention has been made in view of the circumstances described above, and an object of this invention is to provide a lubricating structure of a hybrid vehicle drive device capable of improving the lubricating performance of a change mechanism. gear and a gear reducer mechanism by increasing the amount of the lubricating oil supplied to the gear change mechanism and the gear reducer mechanism and improving the reliability of the gear change mechanism and the gear reducer mechanism .

Summary

There is provided a structure for lubricating a hybrid vehicle drive device comprising: a shift mechanism changing the power transmitted from an internal combustion engine; a differential device including a pinion member receiving power from the shift mechanism and transmitting power from the shift mechanism to the left and right drive wheels; a speed reduction mechanism comprising a plurality of rotary shafts and a plurality of sets of speed reduction gears provided in the plurality of rotary shafts and transmitting rotation of an engine to the speed change mechanism by reducing the rotation, the plurality of rotating shafts being provided to be separated from each other in an up-down direction so that the speed reduction mechanism projects upward from the speed change mechanism; a transmission case storing lubricating oil in a bottom part and accommodating the speed change mechanism, the speed reduction mechanism and the differential device; and an oil trough collecting lubricating oil scraped by the pinion member and supplying the lubricating oil to the shift mechanism, wherein the transmission case includes a plurality of bearing holding portions having an oil circulation space formed therein such that lubricating oil flows therein and rotatably supporting the plurality of rotating shafts through a bearing, wherein the plurality of bearing holding parts includes a lower bearing holding part supporting the rotating shaft located at the lowest position among the plurality of rotating shafts and an upper bearing holding part located above the lower holding part bearing, wherein the oil gutter is provided at a lower part of the speed reducer mechanism so as to catch lubricating oil dispersed from the speed reducing and downward flowing mechanism, and wherein the oil gutter includes an oil supply part supplying lubricating oil to the oil circulation space of the lower part of rolling support.

Thus, according to this invention, it is possible to improve the lubricating performance of the speed change mechanism and the speed reduction mechanism by increasing the amount of lubricating oil supplied to the speed change mechanism and the speed reduction mechanism. shift and improve the reliability of the shift mechanism and the gear reducer mechanism.

The following features can be optionally implemented, separately or in combination with each other:

the oil trough is provided at the same height position as that of the rotating shaft supported by the lower bearing holding part, and

the oil supply part supplies lubricating oil to an axis of the rotary shaft supported by the lower bearing holding part.

the oil gutter includes an oil receiver capturing lubricating oil dispersed from the speed reduction mechanism and flowing downward.

the transmission case includes a peripheral wall portion surrounding the speed reduction mechanism, and

the oil receiver being provided under the peripheral wall portion and catches lubricating oil dispersed from the speed reduction mechanism and flowing down along the peripheral wall portion.

the oil receiver is a first oil receiver, the oil gutter includes a second oil receiver different from the first oil receiver, and

the second oil receiver being angled from a side wall of the oil gutter toward the speed reduction mechanism.

Other characteristics, details and advantages will appear on reading the detailed description below, and on analyzing the appended drawings, in which:

Fig. 1

is a left view of a hybrid vehicle drive device according to one embodiment of the present invention.

Fig. 2

is a rear view of the hybrid vehicle drive device according to one embodiment of the present invention.

Fig. 3

is a skeleton view of the hybrid vehicle drive device according to one embodiment of the present invention.

Fig. 4

is a left view of the hybrid vehicle drive device according to an embodiment of the present invention in a state in which a cover is removed therefrom.

Fig. 5

is a cross-sectional view along the direction VV of FIG. 1.

Fig. 6

is a perspective view of the cover of the hybrid vehicle drive device according to one embodiment of the present invention.

Fig. 7

is a perspective view of an upper portion of a left crankcase of the hybrid vehicle drive device according to one embodiment of the present invention.

Fig. 8

is a cross-sectional view along the direction VIII-VIII of FIG. 1.

Fig. 9

is a cross-sectional view seen from a direction IX-IX of FIG. 4 in a state in which the cover is attached.

Fig. 10

is a cross-sectional view along the direction XX of FIG. 1.

Fig. 11

is a longitudinal sectional view in which the cover of the hybrid vehicle drive device according to an embodiment of the present invention is cut by an oil passage.

Fig. 12

is a perspective view of an oil drain of the hybrid vehicle drive device according to one embodiment of the present invention.

Fig. 13

is a plan view of the oil gutter of the hybrid vehicle drive device according to one embodiment of the present invention.

The figures and the following detailed description essentially contain precise elements. They can be used to enhance understanding of the disclosure and also to define the invention if necessary.

A lubricating structure of a hybrid vehicle drive device according to embodiments of this invention includes: a shift mechanism modifying the power transmitted from an internal combustion engine; a differential device including a pinion member receiving power from the shift mechanism and transmitting power from the shift mechanism to the left and right drive wheels; a speed reduction mechanism comprising a plurality of rotary shafts and a plurality of sets of speed reduction gears provided in the plurality of rotary shafts and transmitting rotation of an engine to the speed change mechanism by reducing the rotation, the plurality of rotating shafts being provided to be separated from each other in an up-down direction so that the speed reduction mechanism projects upward from the speed change mechanism; a transmission case storing lubricating oil in a bottom part and accommodating the speed change mechanism, the speed reduction mechanism and the differential device; and an oil trough collecting lubricating oil scraped by the pinion member and supplying the lubricating oil to the shift mechanism, wherein the transmission case includes a plurality of bearing holding portions having an oil circulation space formed therein such that lubricating oil flows therein and rotatably supporting the plurality of rotating shafts through a bearing, wherein the plurality of bearing holding parts includes a lower bearing holding part supporting the rotating shaft located at the lowest position among the plurality of rotating shafts and an upper bearing holding part located above the lower holding part bearing, wherein the oil gutter is provided at a lower part of the speed reducer mechanism so as to catch lubricating oil dispersed from the speed reducing and downward flowing mechanism, and wherein the oil gutter includes an oil supply part supplying lubricating oil to the oil circulation space of the lower part of rolling support.

Accordingly, the lubricating structure of the hybrid vehicle drive device according to embodiments of this invention can improve the lubricating performance of the shift mechanism and the speed reducer mechanism by increasing the amount of lubricating oil. provided to the shift mechanism and the gear reducer mechanism and improves the reliability of the gear shift mechanism and the gear reducer mechanism.

Hereinafter, the lubricating structure of the hybrid vehicle drive device according to embodiments of the present invention is described with reference to the drawings.

Figs. 1 to 13 are diagrams illustrating the lubricating structure of the hybrid vehicle driving device according to embodiments of this invention.

In Fig. 1 to 13, the up, down, forward, backward, left and right directions are the up, down, forward, backward, left and right directions of the hybrid vehicle driving device provided in the vehicle, the direction orthogonal to the front-rear direction is the left-right direction, and the direction along the height of the hybrid vehicle driving device is the up-down direction.

First, a configuration is described.

In Fig. 1, a hybrid vehicle (hereinafter simply referred to as a vehicle) 1 comprises a vehicle body 2, and the vehicle body 2 is divided into a front engine compartment 2A and a rear vehicle interior 2B by an instrument panel 3. The compartment Engine 2A is equipped with a hybrid vehicle drive device (hereinafter simply referred to as drive device) 4, and drive device 4 has six forward shift ratios and one reverse shift ratio.

As illustrated in Fig. 2, the drive device 4 comprises a transmission case 5, and the transmission case 5 comprises a right case 6, a left case 7 and a cover 27 in sequential order from the right side.

A heat engine 8 is connected to the right end of the right crankcase 6. The heat engine 8 includes a crankshaft 9 (see Fig. 3) and the crankshaft 9 is provided so as to extend in the width direction of the vehicle. 1. That is, the heat engine 8 of this embodiment is configured as a horizontally placed heat engine, and the vehicle 1 of this embodiment is a front heat engine/front wheel drive (FF) vehicle. . The heat engine 8 of this embodiment is configured as an internal combustion engine.

The left casing 7 is connected to the side opposite the heat engine 8 with respect to the right casing 6. That is to say that the left casing 7 is connected to the left side of the right casing 6. As illustrated in FIG. 2, a flange portion 6F is formed in the left outer peripheral edge of the right crankcase 6.

As illustrated in Fig. 2, a flange portion 7F is formed in the right outer peripheral edge of the left crankcase 7. The flange portion 6F of the right crankcase 6 and the flange portion 7F of the left crankcase 7 are joining portions of the right crankcase 6 and the left crankcase 7 and the respective end surfaces facing the left and right directions are joining surfaces (mating surfaces) which are joined to each other in an overlapping state.

The flange portion 7F is provided with a plurality of boss portions (not shown) into which bolts 23A (see Fig. 1) are inserted, and the flange portion 6F is provided with a plurality of boss portions (not shown). illustrated) which correspond to the boss portions of the flange portion 7F.

In the transmission case 5, the bolt 23A is tightened on the boss part of the flange part 6F and the boss part of the flange part 7F so that the right crankcase 6 and the left crankcase 7 are fixed and integrated. to one another. The cover 27 is fixed to the left end of the left casing 7 by a bolt 23B.

The right casing 6 houses a clutch 10 (see Fig. 3). The left casing 7 houses an input shaft 11, a forward gear output shaft 12, a reverse gear output shaft 13 and a differential device 15 illustrated in FIG. 3. The input shaft 11, forward output shaft 12 and reverse output shaft 13 are provided in parallel in the left-right direction of the vehicle.

As illustrated in Fig. 3, the input shaft 11 is connected to the thermal engine 8 via the clutch 10 and the power of the thermal engine 8 is transmitted via the clutch 10. The input shaft 11 comprises a first input pinion gear 16A, a second gear ratio input gear 16B, a third gear ratio input gear 16C, a fourth gear ratio input gear 16D, a fifth gear ratio input gear 16E gear and a 16F sixth gear input gear.

Input gears 16A and 16B are fixed to input shaft 11 and rotate together with input shaft 11. Input gears 16C to 16F are provided rotatably relative to the shaft. input 11.

The forward gear output shaft 12 includes a first gear ratio output gear 17A, a second gear ratio output gear 17B, a third gear ratio output gear 17C, a fourth gear ratio output gear gear 17D, a fifth gear ratio output gear 17E, a sixth gear ratio output gear 17F, and a forward final drive gear 17G and the output gears 17A to 17F mesh with the input gears 16A to 16F constituting the same gear change ratio.

The output gears 17A and 17B are provided rotatably relative to the forward gear output shaft 12. The output gears 17C to 17F and the final drive gear 17G are fixed to the forward gear output shaft 12 and rotate together with the forward output shaft 12.

In a first gear ratio, the power of heat engine 8 is transmitted from input shaft 11 to forward output shaft 12 via input pinion 16A and output pinion 17A. In a second gear ratio, the power of heat engine 8 is transmitted from input shaft 11 to forward output shaft 12 via input pinion 16B and output pinion 17B.

A first synchronization device 18 is provided on the forward output shaft 12 between the output gear 17A and the output gear 17B.

When the first synchronizer 18 is moved to a first gear ratio by a shift operation, the first gear ratio output gear 17A is connected to the forward gear output shaft 12. Then, when the first synchronization device is shifted to a second gear ratio by a shift operation, the second gear ratio output gear 17B is connected to the forward gear output shaft 12. Accordingly, the output gear 17A or output gear 17B rotates with forward output shaft 12.

A second synchronization device 19 is provided on the input shaft 11 between the input pinion 16C and the input pinion 16D.

When the second synchronizer 19 is shifted to a third speed ratio by a shift operation, the input gear 16C is connected to the input shaft 11. Then, when the second synchronizer is shifted to a fourth gear ratio by a shift operation, the input gear 16D is connected to the input shaft 11. Accordingly, the input gear 16C or the input gear 16D rotates with the input shaft 11.

In a third gear ratio, the power of heat engine 8 is transmitted from input shaft 11 to forward output shaft 12 via input pinion 16C and output pinion 17C. In a fourth gear ratio, the power of heat engine 8 is transmitted from input shaft 11 to forward output shaft 12 via input pinion 16D and output pinion 17D.

A third synchronization device 20 is provided on the input shaft 11 between the input pinion 16E and the input pinion 16F.

When the third synchronizer 20 is shifted to a fifth speed ratio by a shift operation, the input gear 16E is connected to the input shaft 11. Then, when the third synchronizer is shifted to a sixth gear ratio by a shift operation, the input gear 16F is connected to the input shaft 11. Accordingly, the input gear 16E or the input gear 16F rotates with the input shaft 11.

In a fifth gear ratio, the power of heat engine 8 is transmitted from input shaft 11 to forward output shaft 12 via input pinion 16E and output pinion 17E. In a sixth gear ratio, the power of heat engine 8 is transmitted from input shaft 11 to forward output shaft 12 via input pinion 16F and output pinion 17F.

The reverse gear output shaft 13 is provided with a reverse gear 22A and a reverse final drive gear 22B. The reverse gear 22A is provided rotatably relative to the reverse gear output shaft 13 and meshes with the output gear 17A. Final drive gear 22B is attached to reverse output shaft 13 and rotates with reverse output shaft 13.

The reverse gear output shaft 13 is provided with a fourth synchronizing device 21. When the fourth synchronizing device 21 is shifted to a reverse gear by a shift operation, the reverse gear 22A is connected to the reverse gear output shaft 13. Accordingly, the reverse gear 22A rotates together with the reverse gear output shaft 13.

In a reverse gear, the power of the heat engine 8 is transmitted from the input shaft 11 to the reverse gear output shaft 13 through the input gear 16A, the output gear 17A rotating relative to the forward gear output shaft 12, and the reverse gear 22A.

The forward gear final drive gear 17G and the reverse gear final drive gear 22B mesh with a final driven gear 15A of the differential device 15. Accordingly, the power of the forward gear output shaft 12 and the The reverse gear output 13 is transmitted to the differential device 15 via the forward gear final drive gear 17G or the reverse gear final drive gear 22B.

The differential device 15 includes the final driven pinion 15A, a differential case 15B of which an outer peripheral part is attached to the final driven pinion 15A, and a differential mechanism 15C provided in the differential case 15B. The final driven gear 15A of this embodiment constitutes a gear member of this invention.

First end portions of the left and right drive shafts 24L and 24R are connected to the differential mechanism 15C and the other end portions of the left and right drive shafts 24L and 24R are respectively connected to the left drive wheels and right 40L and 40R. Differential device 15 distributes power from heat engine 8 to left and right drive shafts 24L and 24R through differential mechanism 15C and transmits power to drive wheels 40L and 40R.

Input shaft 11, forward output shaft 12, input gears 16A to 16F and output gears 17A to 17F of this embodiment constitute a shift mechanism 40.

As illustrated in Fig. 2, an electric motor 32 is provided in an upper part of the left casing 7. The electric motor 32 comprises a motor casing 32A and a motor shaft 32B (see Fig. 3) rotatably supported by the motor casing 32A. A rotor and a stator having a coil wound thereon (not shown) are housed inside the motor housing 32A and the motor shaft 32B is integrated with the rotor.

The electric motor 32 generates a rotating magnetic field which rotates in the circumferential direction when a three-phase alternating current is supplied to the stator coil. The stator rotates the rotor integrated in the motor shaft 32B by linking the magnetic flux generated to the rotor.

In the transmission case 5, a reduction gear case part 25 is formed by the left case 7 and the cover 27. As shown in Fig. 1, 3 and 4, the reduction gear case part 25 is formed by the upper part of the cover 27 and a case part 26 formed by extending the left end part of the left case 7 upward. The reduction gear housing part 25 houses a speed reduction mechanism 33 (see Fig. 4).

That is, the left crankcase 7 includes the crankcase part 26 provided at the left end part so as to bulge upward and the opening of the left end part of the left crankcase 7 is enlarged upward by the housing part 26. The housing part 26 is a housing part which accommodates the speed reducer mechanism 33, and the speed reducer mechanism 33 is disposed at the left side thereof.

As illustrated in Figs. 1 and 2, the cover 27 is joined (fixed) to the left end part of the left casing 7 by the bolt 23B and blocks the opening of the left end part of the left casing 7 comprising a part of the housing 26. Then, the upper part of the cover 27 is disposed at the left side of the speed reduction mechanism 33 and constitutes the reduction gear housing part 25 forming a housing space for the speed reduction mechanism 33 from the sides left and right with housing part 26.

As illustrated in Fig. 3, the speed reduction mechanism 33 comprises an input shaft 34 connected to the motor shaft 32B of the electric motor 32, a first intermediate shaft 35, a second intermediate shaft 36 and the fourth speed ratio output pinion 17D provided in the forward output shaft 12.

As illustrated in Fig. 10, the input shaft 34 is provided with a mounting groove 34a, an inner peripheral surface of which is provided with a spline, and the front end portion of the motor shaft 32B is spline fitted with the mounting groove. assembly 34a.

As illustrated in Fig. 3, the input shaft 34 is provided with a first drive gear 34A and the first intermediate shaft 35 is provided with a first driven gear 35A and a second driven gear 35B. The second intermediate shaft 36 is provided with a second driven pinion 36A and a third driving pinion 36B.

The first driven gear 35A is formed to have a diameter greater than the diameter of the first drive gear 34A and meshes with the first drive gear 34A. The second drive gear 35B is disposed at the left side of the first driven gear 35A, is formed to have a diameter smaller than the diameters of the first driven gear 35A and the second driven gear 36A, and meshes with the second driven gear 36A.

The third drive gear 36B is disposed on the right side of the second driven gear 36A with the first driven gear 35A interposed therebetween. The third drive gear 36B is formed to have a diameter substantially the same as the diameter of the second driven gear 36A and greater than the diameter of the fourth gear ratio output gear 17D and meshes with the fourth gear ratio output gear 17D.

Since the diameters of the driving gears 34A, 35B and 36B and the driven gears 35A and 36A are set to have an arbitrary speed reduction ratio, the speed reduction mechanism 33 reduces the power of the electric motor 32 and transmits the power to the forward output shaft 12.

The first drive gear 34A and the first driven gear 35A of this embodiment constitute a first set of speed reduction gears 37 and the second drive gear 35B and the second driven gear 36A constitute a second set of speed reduction gears 38 The third drive gear 36B and the output gear 17D constitute a third set of speed reduction gears 39 and these sets of speed reduction gears 37, 38 and 39 constitute a set of speed reduction gears of the present invention. . Further, sprockets having different diameters and arranged coaxially also contribute to a reduction in speed as with the first driven gear 35A and the second driven gear 35B.

A damper 81 is disposed at the left end portion of the second intermediate shaft 36 so as to be coaxial with the second intermediate shaft 36. As shown in FIG. 9, the shock absorber 81 comprises an outer cylinder 82 fitted to the second driven gear 36A so as to rotate together, an inner cylinder 86 fitted and fixed to the second intermediate shaft 36, and an elastic member 85 provided between the outer cylinder 82 and inner cylinder 86.

The outer cylinder 82 is splined to the outer peripheral portions of the second driven gear 36A and to the inner cylinder 86 at the inner peripheral portion of the side of the second driven gear 36A in the axial direction.

In the spline fitting portion 88, the outer cylinder 82 and the second driven gear 36A are spline fitted to each other without a gap. That is, the spline of the outer cylinder 82 is fitted to the spline of the second driven gear 36A at the spline fitting portion 88 with no gap in the direction of rotation so that the outer cylinder 82 and the second driven gear 36A rotate together.

The outer cylinder 82 and the inner cylinder 86 are spline-fitted to each other at the spline-fitting portion 89 while having a relatively large gap in the direction of rotation so as to be slightly relatively movable. in rotation. That is, the spline adjustment portion 89 regulates the relative rotation between the outer cylinder 82 and the inner cylinder 86 within a predetermined range and transmits power from the outer cylinder 82 to the inner cylinder 86 without passing through the elastic element 85 in a state in which the relative rotation is regulated and the splines are in contact with each other.

A bearing (metal ring) is arranged between the second driven pinion 36A and the second intermediate shaft 36 and the second driven pinion 36A comprises an adjustment part 87 supported axially by the second intermediate shaft 36 so as to be rotatable relative to this one. Here, the relative rotation at the barbed fitting portion 89 is regulated to be within a predetermined range and the second driven gear 36A allows relative rotation with respect to the second countershaft 36 by a degree of variation of rotation of the gear. in accordance with a variation of rotation of the heat engine by deforming the elastic element 85.

The damper 81 (the elastic member 85) effectively absorbs rotational variation and differential rotation of different power sources such as the heat engine 8 and the electric motor 32 and suppresses rattling noise between the gears of the input shaft 34, first intermediate shaft 35 and second intermediate shaft 36.

As illustrated in Fig. 2, 4 and 9, the housing part 26 constituting the reduction gear housing part 25 comprises a peripheral wall part 28. The peripheral wall part 28 projects from a peripheral edge of a wall part 29 (described later) of the left crankcase 7 in a leftward direction (a direction away from the right crankcase 6) and its upper end 28a (see Fig. 4) extends upward relative to an upper wall 7B of the left crankcase 7. Further, the upper wall 7B is a part other than the crankcase part 26 and is a ceiling wall part of the left crankcase 7 in a part in which the speed reduction mechanism 33 does not exist and the shift mechanism 40 is arranged.

As illustrated in Fig. 4, viewed from the axial direction of the input shaft 11, the peripheral wall portion 28 is formed from the front side of the speed reducer mechanism 33 to its rear side via the upper side and surrounds the periphery of the mechanism speed reducer 33 excluding the lower side.

As illustrated in Fig. 6, cover 27 includes a side wall portion 27A and a peripheral wall portion 27B. As illustrated in Fig. 8, the side wall part 27A is a vertical wall which is perpendicular to the left-right direction and forms a left surface of the transmission case 5, the peripheral wall part 27B is projected from the side wall part 27A in the direction of the peripheral wall part 28 so as to correspond to the peripheral wall part 28 of the left crankcase 7, and a front end part 27a in the projection direction is joined to a front end part 28b of the peripheral wall 28 in the projection direction.

Further, in the description of the peripheral wall part 28 of the left crankcase 7, a description is made by indicating a part of the reduction gear housing part 25. However, a peripheral edge part of the left opening of the left crankcase 7 exists so as to be continuous to the peripheral wall portion 28 and the peripheral edge portion is provided with a joining surface which is continuous to the joining surface between the front end portion 27a of the peripheral wall 27B of the cover 27 and the front end part 28b of the peripheral wall part 28. At the joint surface, the cover 27 is joined (fixed) to the left end part of the left casing 7 by the bolt 23B and the cover 27 blocks the opening of the left end part of the left casing 26 comprising a part other than the casing part 26.

That is, the cover 27 is fixed to the peripheral wall part 28 by the bolt 23B (see Fig. 1) while the front end part 27a in the projection direction overlaps the end part front 28b of the peripheral wall part 28 in the projection direction so that the opening end of the peripheral wall part 28 is blocked.

As illustrated in Figs. 2, 4 and 8, the left crankcase 7 includes the wall part 29. The wall part 29 is a vertical wall which is perpendicular to the axial direction (the left-right direction) and is formed as a body with the left crankcase 7 As illustrated in FIG. 8, the wall part 29 is provided between the speed reducer mechanism 33 and the electric motor 32 in the axial direction of the input shaft 34, and the speed reducer mechanism 33 is provided between the wall part 29 and the cover 27 in the axial direction of the input shaft 34.

As illustrated in Fig. 2 and 8, the wall part 29 includes a vertical wall part 29A which extends upward from the upper wall 7B of the left case 7 and becomes the right side wall of the reduction gear case part 25 and a partition wall part 29B which is an inner partition wall of the left crankcase 7 extending downward from the upper wall 7B of the left crankcase 7 so as to be continuous from the lower part of the wall part vertical 29A and connects the upper wall 7B and a lower part 28c (see Fig. 4) of the left casing 7.

The wall part 29 of this embodiment includes the vertical wall part 29A and the partition wall part 29B, and the vertical wall part 29A and the partition wall part 29B are formed as a body with the left crankcase 7. Then, a part above the upper wall 7B with respect to the upper wall 7B of the left crankcase 7 as a boundary constitutes the vertical wall part 29A, and a part below the upper wall 7B constitutes the dividing wall 29B.

As illustrated in Fig. 5, the partition wall portion 29B is formed inside the left crankcase 7 forward from the vicinity of the center of the left and right directions of the rear wall of the left crankcase 7. As shown in FIG. 4, the partition wall portion 29B passes over the forward output shaft 12 and reaches the upper side of the input shaft 11. Further, as shown in FIG. 9, the gear reducer housing chamber 30B is formed as a space between the cover 27 and the wall portion 29.

As illustrated in Fig. 4, the front lower position inside the left crankcase 7 is not provided with the partition wall part 29B, but is provided with an opening part 29h in which the input shaft 11 and l forward output shaft 12 are arranged. As illustrated in Fig. 5, the input shaft 11 and the forward output shaft 12 pass through the opening portion 29b and extend from the right crankcase 6 toward the speed reduction mechanism accommodating chamber 30B.

The input gears 16A, 16B and 16C and the output gears 17A, 17B and 17C are provided in a gear accommodating chamber 30A located on the side of the right crankcase 6 with respect to the partition wall part 29B, and , the input gears 16D, 16E and 16F, the output gears 17D, 17E and 17F and the speed reducer mechanism 33 are provided in the housing chamber of the speed reducer mechanism 30B located on the side of the cover 27 with respect to to partition wall portion 29B.

As illustrated in Fig. 2 and 4, the electric motor 32 generating travel driving power is attached to the right side of the housing part 26. In order to attach the electric motor 32, the upper part of the vertical wall part 29A is provided with 29C engine attachment part turned to the right. The motor attachment part 29C is formed into a disc shape having the same outer diameter as the outer diameter of the electric motor 32, i.e. the outer diameter of the motor housing 32A.

The outer peripheral part of the motor mounting part 29C is provided with a plurality of boss parts 29m, and the boss parts 29m are provided along the outer peripheral part of the motor mounting part 29C. A bolt 23C (see Fig. 1) is inserted through the motor attachment part 29C and the bolt 23C is tightened in a threaded hole (not shown) formed in the motor housing 32A, so that the electric motor 32 is attached to the engine attachment portion 29C.

As illustrated in Fig. 1, the rear part of the right end part of the electric motor 32 is provided with a motor connector 32C, and a power cable (not shown) for driving the electric motor 32 is connected to the motor connector 32C.

The upper part of the electric motor 32 is provided with a cooling water introduction pipe 32a and a cooling water delivery pipe 32b. The cooling water introduction conduit 32a introduces cooling water into the electric motor 32 and the cooling water discharge conduit 32b discharges the cooling water having cooled the electric motor 32 from the electric motor 32 .

As illustrated in Fig. 1 and 2, the transmission casing 5 is provided with a front support 46A and a rear support 46B. The front bracket 46A connects the front edge portion of the electric motor right end portion 32 to the right crankcase 6 and supports the electric motor right end portion 32 to the right crankcase 6.

The rear bracket 46B connects the rear edge portion of the right end portion of the electric motor 32 to the right crankcase 6 and supports the electric motor 32 to the right crankcase 6. In this way, the left side of the electric motor 32 is connected to the engine mounting part 29C and the right side thereof is connected to the right crankcase 6.

As illustrated in Fig. 8 and 9, the wall part 29 of the left casing 7 is provided with bearing holding parts 29D, 29E and 29F. The bearing holding portions 29D and 29E extend in a cylindrical shape from the vertical wall portion 29A towards the cover 27 and include the vertical wall portion 29A. The bearing holding part 29F extends in a cylindrical shape from the partition wall part 29B towards the cover 27 and includes the partition wall part 29B.

The side wall part 27A of the cover 27 is provided with cylindrical bearing holding parts 27C, 27D and 27E. Bearing holding portions 27C, 27D, and 27E extend cylindrically from side wall portion 27A toward vertical wall portion 29A and include side wall portion 27A.

As illustrated in Fig. 8, the right end portion of the input shaft 34 of the speed reducer mechanism 33 is rotatably supported by the bearing holding portion 29D via a ball bearing 51A and the left end portion of the The input shaft 34 of the speed reduction mechanism 33 is rotatably supported by the bearing holding part 27C via a ball bearing 51B. The inner diameter dimension of the ball bearing 51A is formed to be larger than the inner diameter dimension of the ball bearing 51B.

The opening end of the bearing holding part 29D (the opening end on the side of the electric motor 32 with respect to the ball bearing 51A) is provided with an oil seal 55 and the outer peripheral part of the right end part of the input shaft 34 is in contact with the inner peripheral part of the oil seal 55. In other words, the right end part of the the input shaft 34 projects from the housing chamber of the speed reducer mechanism 30B. Accordingly, the motor shaft 32B can be splined fit to the fit groove 34a formed at the axis of the right end portion of the input shaft 34 while sealing the housing chamber of the speed reduction mechanism 30B by means of the oil seal 55. The oil seal 55 of this embodiment forms part of the vertical wall portion 29A.

An oil circulation space 53A through which the lubricating oil circulates is formed inside the bearing holding part 29D. The oil circulation space 53A is formed as a space surrounded by the bearing holding part 29D, the oil seal 55 (the vertical wall part 29A of the bearing holding part 29D) and the right end portion of the input shaft 34 and the ball bearing 51A is provided in the oil circulation space 53A.

An oil circulation space 53B through which the lubricating oil circulates is formed inside the bearing holding part 27C. The oil circulation space 53B is formed as a space surrounded by the bearing holding part 27C, and the left end part of the input shaft 34 and the ball bearing 51B is provided in the oil circulation space 53B.

As illustrated in Fig. 8 and 9, the right end portion of the first intermediate shaft 35 is rotatably supported on the bearing holding portion 29E through a needle bearing 51C and the left end portion of the first intermediate shaft 35 is movably supported in rotation on the bearing holding part 27D via a ball bearing 51D.

An oil circulation space 53C through which the lubricating oil circulates is formed inside the bearing holding portion 29E. The oil circulation space 53C is formed as a space surrounded by the bearing holding part 29E, and the right end part of the first intermediate shaft 35 and the needle bearing 51C is provided in the space oil circulation temperature 53C.

An oil circulation space 53D through which the lubricating oil circulates is formed inside the bearing holding part 27D. The oil circulation space 53D is formed as a space surrounded by the bearing holding part 27D, and the left end part of the first intermediate shaft 35 and the ball bearing 51D is provided in the space of oil circulation 53D.

As illustrated in Fig. 9, an oil circulation space 53E through which the lubricating oil circulates is formed inside the bearing holding portion 29F. The oil circulation space 53E is formed as a space surrounded by the bearing holding part 29F, and the right end part of the second intermediate shaft 36 and a ball bearing 51E is provided in the space. oil circulation space 53E.

An oil circulation space 53F through which the lubricating oil circulates is formed inside the bearing holding portion 27E. The oil circulation space 53F is formed as a space surrounded by the bearing holding part 27E, and the left end part of the second intermediate shaft 36 and a ball bearing 51F is provided in the space. 53F oil circulation space.

In this way, the input shaft 34, the first intermediate shaft 35 and the second intermediate shaft 36 are rotatably supported on the wall part 29 and the cover 27 by the ball bearings 51A, 51B, 51D, 51E and 51F and the needle bearing 51C.

The ball bearings 51A, 51B, 51D, 51E and 51F and the needle bearing 51C of this embodiment constitute a bearing of this invention.

As illustrated in Fig. 7 and 8, a semicircular concave part 29M is formed between the bearing holding part 29D and the bearing holding part 29E, and the bearing holding part 29E is located at the lower end of the concave part 29M.

As illustrated in Fig. 8, the bearing holding part 29D and the bearing holding part 29E are provided side by side in the up-down direction orthogonal to the input shaft 34. In other words, the bearing holding part 29D and the bearing holding portion 29E are formed at the same position in the axial direction of the input shaft 34. As shown in FIG. 9, the bearing holding part 27E is provided at a separate position from the vertical wall part 29A relative to the bearing holding part 27D in the axial direction of the input shaft 34.

The bearing holding part 29F is provided at a separate position from the cover 27 relative to the bearing holding part 29E in the axial direction of the second intermediate shaft 36. The third driving gear 36B is arranged at the same position as that of the bearing holding part 29E in the axial direction of the second intermediate shaft 36 and the third driving gear 36B is provided so as to plunge under the bearing holding part 29E.

Specifically, a pinion housing part 29G in which the partition wall part 29B is recessed into a cylindrical shape toward the right crankcase 6 is provided under the bearing holding part 29E of the partition wall part 29B. and near the bearing holding part 27E with respect to the bearing holding part 29F and the third driving gear 36B is accommodated in the pinion housing part 29G.

Here, the reason why the right end portion of the first intermediate shaft 35 is supported on the bearing holding portion 29E by the needle bearing 51C is described.

When the third drive gear 36B is provided so as to plunge under the bearing holding portion 29E, the axial length of the input shaft 34 and the first intermediate shaft 35 can be shortened and the size of the transmission case 5 can be be reduced with respect to the axial direction of the input shaft 34 and the first intermediate shaft 35.

In other words, in the input shaft 34, the first intermediate shaft 35 and the second intermediate shaft 36, the ball bearings 51A and 51E and the needle bearing 51C are arranged in the same wall part 29, but when the positions of the ball bearing 51A and the needle bearing 51C of the input shaft 34 and the first intermediate shaft 35 are arranged near the cover 27 relative to the position of the ball bearing 51E of the second intermediate shaft 36, the axial length of the input shaft 34 and the first intermediate shaft 35 can be shortened. As a result, these shafts have advantageous strength or stiffness.

Further, the third drive gear 36B can be disposed on the side of the right case 6 relative to the first driven gear 35A, and the transmission case 5 can be reduced in size in the axial direction. Further, the third drive gear 36B can mesh with the output gear 17D disposed near the center of the forward output shaft 12 in the axial direction.

Incidentally, if the ball bearing is used instead of the needle bearing 51C when the third drive gear 36B is provided to dip under the bearing holding portion 29E in consideration of a decrease in size in the axial direction , the bearing increases in size, and the bearing holding portion 29E holding this bearing increases in size in the up-down direction. Then, there arises a problem that the enlarged bearing holding portion 29E interferes with the third driving gear 36B.

Thus, the bearing holding part 29E and the bearing holding part 29F are separated from each other in the up-down direction, and the first intermediate shaft 35 and the second intermediate shaft 36 are provided so as to be separated from each other in the up-down direction. Accordingly, it is possible that the transmission case 5 increases in size in the up-down direction.

In contrast, according to the drive device 4 of this embodiment, since the right end portion of the first intermediate shaft 35 is rotatably supported by the bearing holding portion 29E through the needle bearing 51C , the size of the bearing holding portion 29E (the radial dimension from the axis of the first intermediate shaft 35) can be reduced.

For this reason, the bearing holding part 29E and the bearing holding part 29F may be provided adjacently in the up-down direction, and the first intermediate shaft 35 and the second intermediate shaft 36 may be provided adjacently in the up-down direction. Accordingly, it is possible to prevent an increase in the size of the transmission case 5 in the up-down direction.

As illustrated in Fig. 5, the left end portion of the input shaft 11 and the left end portion of the forward output shaft 12 are respectively provided with ball bearings 50A and 50B, and the left end portion of the input shaft 11 and the left end part of the forward output shaft 12 project to the left of the left casing 7 and are respectively supported rotatably by the cover 27 via 50A and 50B ball bearings.

As illustrated in Fig. 9, an oil passage 36a is formed at the axis of the second intermediate shaft 36. The oil passage 36a extends along the axial direction of the second intermediate shaft 36 so as to be open at both ends of this one.

As illustrated in Figs. 1 and 4, the left side wall 7A of the left crankcase 7 is provided with a pump housing part 43 and the pump housing part 43 houses an oil pump 47. The oil pump 47 is provided at the end part of the reverse output shaft 13 (see Fig. 3) and is driven by the reverse output shaft 13.

In other words, the rotation of the final driven gear 15A of the differential device 15 is transmitted to the reverse gear output shaft 13 through the intermediary of the final driving gear 22B and the oil pump 47 is driven by the output shaft of reverse gear 13 when the vehicle is moving.

As illustrated in Fig. 4, the pump housing part 43 is provided with a cylindrical oil discharge passage part 44, and the oil discharge passage part 44 has an oil discharge passage 44a provided therein so as to open toward the inside of the left crankcase 7. The base end portion of the oil passage 48 is inserted into the opening formed in the upper end portion of the oil discharge passage 44a of so that the oil pipe is attached to it.

As illustrated in Fig. 4, the oil duct 48 is routed along the inner surface of the transmission case 5, passes behind the second intermediate shaft 36, the first intermediate shaft 35 and the input shaft 34 of the gear reducer mechanism 33, extends upward, passes over input shaft 34 and extends to the rear side of input shaft 34.

Lubricating oil O is stored in the bottom part of the left crankcase 7, an oil strainer (not shown) is attached to the pump housing part 43, and the lubricating oil from the bottom part of the left crankcase 7 is introduced from the oil strainer to the oil pump 47. The oil pump 47 supplies the lubricating oil introduced into the pump housing part 43 to the oil conduit 48 via the oil discharge passage 44a.

The oil conduit 48 discharges the lubricating oil supplied from the oil pump 47 to the upper side of the input shaft 34. In other words, the oil conduit 48 supplies the lubricating oil supplied from the oil pump 47 at the top of the speed reducer mechanism 33. The oil conduit 48 of this embodiment constitutes an oil passage portion of the present invention.

As illustrated in Fig. 4 and 6, the oil duct 48 is curved from the rear side of the bearing holding part 27C along the peripheral wall part 27B of the cover 27 or the peripheral wall part 28 of the left crankcase 7 so as to to extend forward and the front end portion is open downward.

In other words, the opening of the upper front end of the oil duct 48 is on the front side of the input shaft 34 and is directed between the input shaft 34 and the peripheral wall part 27B or the peripheral wall part 28. The inner peripheral surface of the peripheral wall part 27B of the cover 27 is provided with a rib 27b. The rib 27b is formed along the axial direction of the input shaft 34 and protrudes from the peripheral wall part 27B towards the bearing retaining part 27C.

As illustrated in Fig. 7, the inner peripheral surface of the peripheral wall portion 28 of the left crankcase 7 is provided with a rib 28d. The rib 28d is formed along the axial direction of the input shaft 34 and protrudes from the peripheral wall portion 28 toward the input shaft 34. Further, the position of the rib 28d is defined so that the rib is continuous with the rib 27b while the cover 27 is attached to the left crankcase 7. Further, the rib 28d and the rib 27b are disposed at a higher position than is the axle of input shaft 34 in front of input shaft 34.

The upper opening of the oil duct 48 is open downwards, more precisely in the direction of the ribs 27b and 28d. The lubricating oil flowing out from the front end portion (opening) of the oil duct 48 collides with the ribs 27b and 28d. The lubricating oil colliding with the ribs 27b and 28d is widely dispersed so as to flow down inside the reduction gear case part 25 as the flow speed decreases.

As illustrated in Fig. 6, a guide groove 27g having a notch shape is formed in the bearing holding portion 27C supporting the input shaft 34, located at the highest position among the input shaft 34, the first intermediate shaft 35 and the second intermediate shaft 36. The guide groove 27g is a front part of the bearing holding part 27C and is formed in a range from the axial position of the input shaft 34 to the positions of the ribs 27b and 28d in the height direction.

As illustrated in Fig. 10, the guide groove 27g reaches the oil circulation space 53B and passes through the lateral side of the ball bearing 51B so that the oil circulation space 53B communicates with the peripheral space of the part bearing retainer 27C. The guide groove 27g guides the lubricating oil flowing out of the oil duct 48 to the oil circulation space 53B.

As illustrated in Fig. 7, a guide groove 29g having a notch shape is formed in the bearing holding part 29D supporting the input shaft 34, located at the highest position among the bearing holding parts 29D, 29E and 29F of the wall portion 29 of the left crankcase 7. The guide groove 29g is a front portion of the bearing holding portion 29D and is formed in a range from the axial position of the input shaft 34 to the positions ribs 27b and 28d in the height direction.

As illustrated in Fig. 10, the guide groove 29g reaches the oil circulation space 53A and passes through the lateral side of the ball bearing 51A so that the oil circulation space 53A communicates with the peripheral space of the part bearing retainer 29D. The guide groove 29g guides the lubricating oil flowing out of the oil duct 48 to the oil circulation space 53A.

The input shaft 34, the first intermediate shaft 35 and the second intermediate shaft 36 of this embodiment constitute a rotary shaft of this invention. The bearing retainer portions 27C, 27D, 29D and 29E constitute an upper bearing retainer of this invention and the bearing retainer portions 27E and 29F constitute a lower bearing retainer of this invention.

The ball bearing 51A constitutes a bearing and a first bearing of this invention and the ball bearing 51B constitutes a bearing and a second bearing of this invention. The bearing holder part 29D constitutes an upper bearing holder part and a first upper bearing holder part of this invention rotatably supporting the right end part (an end part) of the shaft. input 34 in the axial direction through the ball bearing 51A and the bearing holding part 27C constitutes an upper bearing holding part and a second upper bearing holding part of this invention movably supporting in rotating the left end portion (the other end portion) of the input shaft 34 in the axial direction through the ball bearing 51B.

As illustrated in Fig. 6 and 7, an oil gutter 60 is provided in the cover 27 and the wall part 29 at the same height positions as those of the bearing holding parts 27C and 29D (see Fig. 4), in other words, at the same height position as that of the input shaft 34. The oil trough 60 is provided in front of the input shaft 34 inside the reduction gear case part 25.

The oil gutter 60 is provided under the ribs 27b and 28d. The oil gutter 60 catches the lubricating oil scattered or flowing down while colliding with the ribs 27b and 28d and guides the lubricating oil so as to supply the lubricating oil to a part. which needs to be lubricated.

As illustrated in Fig. 9 and 10, the oil gutter 60 is a gutter-like component which is open upward and includes a bottom wall, a front wall erected upward from the front end of the bottom wall, and a rear wall erected upward from the rear end of the bottom wall and extends in the axial direction of the input shaft 34. The rear wall of the oil gutter 60 is provided with an oil outlet 60A having a narrow opening width and an oil outlet 60B having a wider opening width than that of the oil outlet 60A.

As illustrated in Fig. 7, the oil outlet 60A is not protruding backward, is formed at the end portion (the right end portion) of the vertical wall portion 29A side by simply notching the rear wall and faces the guide groove 29g of the bearing holding part 29D. The oil gutter 60 receives lubricating oil supplied from the oil duct 48, allows the received lubricating oil to flow from the oil outlet 60A toward the guide groove 29g, and introduces the lubricating oil into the oil circulation space 53A via the guide groove 29g.

Also, the reason why the 60A oil outlet is not protruding rearward is that interference with the first drive gear 34A must be avoided during assembly. In other words, the rear wall of the oil gutter 60 is set at a position close to the first drive gear 34A disposed on the rear side.

As illustrated in Fig. 6, the oil outlet 60B is formed in the shape of a gutter protruding backward from the rear wall of the end part, on the side of the side wall part 27A and faces the guide groove 27g of the bearing retaining part 27D while being partially disposed inside the guide groove 27g. The oil gutter 60 receives the lubricating oil supplied from the oil conduit 48 and introduces the lubricating oil received from the oil outlet 60B to the oil circulation space 53B through the intermediary of the guide groove 27g.

Since the oil outlet 60B is disposed on the left side of the first drive gear 34A, the oil outlet projects rearward from the rear wall so that no interference occurs with the first drive gear 34A during assembly and the oil outlet 60B is closer to the guide groove 27g.

The oil outlet 60A of this embodiment constitutes a first oil outlet of this invention and the oil outlet 60B constitutes a second oil outlet of this invention. The guide groove 29g constitutes a first guide groove of this invention and the guide groove 27g constitutes a second guide groove of this invention.

As illustrated in Fig. 7, the left end portion of the oil gutter 60 (the side end portion of the side wall portion 27A) is provided with an adjustment projection 60a. As illustrated in Fig. 6 and 9, the side wall portion 27A of the cover 27 is provided with a cylindrical fitting hole portion 27f open toward the vertical wall portion 29A, and the fitting protrusion 60a is inserted and fitted into the adjustment hole 27f. In other words, the oil gutter 60 is attached to the transmission while being attached to the cover 27.

As illustrated in Fig. 7 and 9, a rib-shaped placement part 29H which is continuous with the lower part of the guide groove 29g is provided in the vertical wall part 29A of the left crankcase 7 in the front-rear direction and the placement part 29H connects the bearing holding part 29D and the peripheral wall part 28.

The right end part of the oil gutter 60 (the end part on the side of the vertical wall part 29A) is placed on the placement part 29H and is supported by the placement part 29H. Further, since the right end surface of the oil gutter 60 is in contact with a contact surface 29a of the vertical wall portion 29A located above the placement portion 29H, the rightward movement of the oil gutter 60 is prevented and the separation of the adjustment projection 60a from the adjustment hole part 27f is prevented.

In other words, since the oil gutter 60 is disposed near the contact surface 29a of the vertical wall part 29A while the left end part is held by the adjustment hole part 27f and the right end is in contact with the placement part 29H, the oil gutter is supported so as to be sandwiched between the side wall part 27A of the cover 27 and the vertical wall part 29A of the left crankcase 7. The part The side wall part 27A, the adjustment hole part 27f, the vertical wall part 29A and the placement part 29H of this embodiment constitute an oil gutter support part of this invention.

As illustrated in Fig. 9, an oil passage 35a is formed at the axis of the first intermediate shaft 35. The oil passage 35a extends along the axial direction of the first intermediate shaft 35 so as to be open at both ends of this one.

The left end portion of the first intermediate shaft 35 is provided with a guide plate 61. The guide plate 61 includes a disk-shaped plate portion 61A having an opening formed in the center thereof and a cylindrical duct 61B joined to the center of the plate part 61A.

Since the plate portion 61A is attached to the side wall portion 27A of the cowl 27 and contacts a plurality of projections 27t (see Fig. 8) projecting from the side wall portion 27A toward the first intermediate shaft 35 , the plate part 61A forms a space at its left side with respect to the side wall part 27A so that the space becomes an oil circulation space.

The duct part 61B protrudes in a direction perpendicular to the plate part 61A from the center of the plate part 61A towards the right side and is inserted into the oil passage 35a. Then, the duct part 61B allows the oil circulation space 53D to communicate with the oil passage 35a through the center hole of the disc-shaped plate part 61A.

As illustrated in Fig. 9, an outer race 51n of the ball bearing 51D is fixed to the bearing holding part 27D by a circlip 63 and is positioned in the axial direction of the first intermediate shaft 35. An inner race 51m of the ball bearing 51D is fixed to the first intermediate shaft 35 by a circlip 64 and is positioned relative to the first intermediate shaft 35 in the axial direction of the first intermediate shaft 35.

Therefore, the first intermediate shaft 35 is attached to the transmission case 5 while being positioned in the axial direction. In other words, the first intermediate shaft 35 is positioned on the cover 27 by the ball bearing 51D. This positioning is important because the other end portion (the right end portion) of the first intermediate shaft 35 is rotatably supported relative to the wall portion 29 by the needle roller bearing 51C which cannot be positioned in the axial direction.

A cylindrical circlip operating hole portion 27H is formed in the side wall portion 27A of the cover 27 in the vicinity of the bearing holding portion 27D at the upper front side of the ball bearing 51D. The circlip operating hole portion 27H is closed by a cover 65. When the cover 65 is separated from the circlip operating hole portion 27H, the speed reduction mechanism accommodating chamber 30B communicates with the outside. so that the housing chamber of the speed reducer mechanism 30B is accessible from the outside.

When a tool (not shown) is inserted from the circlip operating hole portion 27H into the speed reduction mechanism accommodating chamber 30B in a state in which the cover 65 is separated from the operating hole portion of circlips 27H, the circlip 63 can be enlarged from the outside. Therefore, the ball bearing 51D attached to the first intermediate shaft 35 can be fixed to the bearing holding part 27D. In other words, the first intermediate shaft 35 can be attached to the bearing holding part 27D.

As illustrated in Fig. 11, the side wall portion 27A of the cover 27 is provided with an oil passage 27d. The oil passage 27d extends obliquely to the left and downward from the oil circulation space 53B of the bearing holding part 27C, and the lower end in the extension direction communicates with the 53D oil circulation space.

Further, the oil passage 27d is a hole which is formed by drilling and a cutting tool (drill) used in the processing is used while inclined left and down so as not to interfere with a cylindrical part (a part to which the ball bearing 51B is fitted) of the bearing holding part 27C.

Since the ball bearing 51D is arranged on the left side of the ball bearing 51B, the bearing holding part 27D is arranged on the left side of the bearing holding part 27C, and the oil circulation space 53D is arranged on the left side of the oil circulation space 53B in the left-right direction, the bulging part of the oil circulation space 53D which is bulged to the left so as to communicate with the oil passage 27d can be minimized.

In other words, the oil passage 27d allows the oil circulation space 53B of the bearing holding part 27C to communicate with the oil circulation space 53D of the bearing holding part 27D. Then, the lubricating oil supplied from the oil circulation space 53B to the oil circulation space 53D through the oil passage 27d is introduced from the oil circulation space 53D to the passage oil 35a from the first intermediate shaft 35 through the conduit portion 61B. The oil passage 27d of this embodiment constitutes a communication passage of this invention.

As illustrated in Fig. 4, the transmission case 5 is provided with an oil trough 66. The oil trough 66 is on the upper side of the forward output shaft 12 and is provided at the same height position as that of the second intermediate shaft 36 located at the lowest position among the input shaft 34, the first intermediate shaft 35 and the second intermediate shaft 36.

As illustrated in Fig. 5, the oil gutter 66 extends to the left from the edge of the left crankcase 7 on the side of the right crankcase 6 and reaches the cover 27.

Oil trough 66 includes a first oil trough portion 67, a second oil trough portion 68, and a third oil trough portion 69.

The first oil gutter part 67 is provided in the gear accommodating chamber 30A and extends from the edge of the left crankcase 7 on the side of the right crankcase 6 to the partition wall part 29B along the inner surface of the rear wall of the left crankcase 7.

The second oil trough portion 68 is provided in the gear housing chamber 30A. The second oil gutter part 68 extends in the front-rear direction to the right side of the partition wall part 29B along the partition wall part 29B so as to reach the upper side of the forward output shaft 12 from the left end of the first oil trough part 67 while being bent with respect to the first oil trough part 67.

The third oil trough part 69 passes under the partition wall part 29B and is provided in front of the second intermediate shaft 36 from the gear accommodating chamber 30A to the gear reducer accommodating chamber 30B. The third oil trough portion 69 extends to the cowl 27 while passing over the forward output shaft 12 along the forward output shaft 12 from the front end of the second oil trough part 68 so as to be bent with respect to the second oil trough part 68.

In Fig. 12 and 13, the first oil trough portion 67 includes a bottom wall 67A and side walls 67B and 67C extending upwardly from the front and rear edges of the bottom wall 67A and a first oil 70 having a gutter shape is formed by the bottom wall 67A and the side walls 67B and 67C so as to be open upwards.

The second oil trough portion 68 includes a bottom wall 68A which is continuous to the bottom wall 67A and side walls 68B and 68C which extend upward from the left and right edges of the bottom wall. 68A and are continuous with the side walls 67B and 67C and a second oil passage 71 is formed in the form of a gutter so as to be opened upward by the bottom wall 68A and the side walls 68B and 68C and to communicate with the first passage of oil 70.

The third oil trough portion 69 includes a bottom wall 69A which is continuous to the bottom wall 68A and side walls 69B and 69C which extend upward from the front and rear edges of the bottom wall. 69A and are continuous with the side walls 68B and 68C and a third oil passage 72 is formed in the form of a gutter so as to be opened upward by the bottom wall 69A and the side walls 69B and 69C and to communicate with the second oil passage 71.

The right end portion of the first oil trough portion 67 is disposed at the front and upper sides of the final driven gear 15A, and the right end portion of the first oil trough portion 67 is provided with an oil introduction part 67D which is open to the rear. Then, the lubricating oil which is scraped by the final driven gear 15A is introduced into the oil introducing part 67D (the first oil trough part 67).

The lubricating oil introduced from the oil introducing part 67D into the first oil trough part 67 flows through the first oil passage 70 toward the second oil passage 71. lubricating oil flowing through the first oil passage 70 toward the second oil passage 71 is guided from the first oil passage 70 to the third oil passage 72 through the second oil passage oil 71.

The left side wall 68C of the second oil trough part 68 is provided with a cylindrical conduit part 68D. The duct part 68D projects to the left from the side wall 68C so that the axis follows the left-right direction and the lubricating oil inside the second oil passage 71 can escape. flow through the inner orifice of conduit portion 68D.

As illustrated in Fig. 9, the conduit portion 68D enters the partition wall portion 29B and is inserted into the oil passage 36a of the second intermediate shaft 36. The second oil passage 71 communicates with the oil passage 36a through the conduit portion 68D and the lubricating oil flowing through the second oil passage 71 is introduced into the oil passage 36a through the conduit portion 68D.

In this way, the oil gutter 66 comprises the conduit part 68D which supplies the lubricating oil to the oil passage 36a formed at the level of the axis of the second intermediate shaft 36 located at the lowest position.

In Fig. 12 and 13, the side walls 69B and 69C of the third gutter part 69 are respectively provided with oil receivers 69D and 69E. The oil receivers 69D and 69E have a shape configured to increase the amount of lubricating oil from the third oil trough part 69 and take the lubricating oil flowing down from the housing chamber of the speed reducer mechanism 30B by the oil gutter 66. The oil receivers 69D and 69E respectively extend obliquely upward so as to protrude upward while being extended in the forward and backward directions of the walls 69B and 69C and are formed with a predetermined dimension in the axial direction of the input shaft 11 as shown in FIG. 5.

As illustrated in Fig. 4, the third oil trough part 69 is disposed under the front peripheral wall part 28. The upper end of the oil receiver 69D is located below the upper wall 7B located at the front of the peripheral wall 28, is provided so as to approach the inner surface (lower surface) of the upper wall 7B, receives the lubricating oil dispersed from the speed reducing mechanism 33 and flowing down along the part peripheral wall 28, and guides the lubricating oil to the third oil passage 72.

Furthermore, as illustrated in Fig. 6, the side wall portion 27A of the cowl 27 is provided with a cylindrical circlip operating hole portion 27H which is formed so as to protrude into the speed reduction mechanism accommodating chamber 30B and the oil Lubrication is accumulated toward the peripheral wall portion 28 on the circular upper surface of the circlip operating hole portion 27H, thereby effectively capturing the lubricating oil.

An oil receiver 69E is provided on the side of the second countershaft 36 with respect to the oil receiver 69D and extends so as to bulge rearwardly from the side wall 69B towards the speed reduction mechanism 33 and to be tilted upward along the outer diameter of the second driven gear 36A.

Specifically, the oil receiver 69E is inclined from the side wall 69C toward the meshing portion between the second drive gear 35B and the second driven gear 36A, receives oil dispersed from the second drive gear 35B and from the second driven gear 36A, and guides the lubricating oil to the third oil passage 72.

Oil receiver 69D of this embodiment constitutes a first oil receiver of this invention and oil receiver 69E constitutes a second oil receiver of this invention.

As illustrated in Fig. 12 and 13, the left end portion of the third oil trough portion 69 is provided with oil supply portions 69F and 69G.

As illustrated in Fig. 5, the oil supply part 69F supplies the lubricating oil from the third oil passage 72 to the ball bearing 50A provided in the input shaft 11. The oil supply part 69G supplies the lubricating oil from the third oil passage 72 to the ball bearing 50B provided in the forward output shaft 12. Although not shown in the drawings, the oil supply parts 69F and 69G are inserted into lubricating grooves communicating with the bearing holding portions for the ball bearings 50A and 50B formed in the cover 27.

As illustrated in Fig. 12 and 13, the side walls 69B and 69C of the third oil channel part 69 are provided with notches 69b and 69c and the notches 69b and 69c are located on the side of the second oil channel part 68 by compared to 69D and 69E oil receivers.

The lower ends of notches 69b and 69c are located below the upper ends of side walls 69B and 69C. Accordingly, part of the lubricating oil flowing through the third oil passage 72 flows out of the notches 69b and 69c.

As illustrated in Fig. 5, the notches 69b and 69c are located between the second synchronizing device 19 and the third synchronizing device 20 in the axial direction of the input shaft 11, and the lubricating oil discharged from the notches 69b and 69c is supplied to the second synchronization device 19, to the third synchronization device 20, to the meshing part between the third drive pinion 36B and the output pinion 17D, to the meshing part between the input pinion 16D and the output 17D, and the meshing part between the input pinion 16E and the output pinion 17E. In other words, the notches 69b and 69c are formed above a part which needs to be lubricated and are arranged close to the right side of the oil receivers 69D and 69E.

In this way, the oil trough 66 of this embodiment catches both the oil scraped by the final driven gear 15A and the oil dispersed from the gear reducer mechanism 33 and flowing downward.

As illustrated in Fig. 12 and 13, an adjustment projection 68a is provided in front of the duct portion 68D of the side wall 68C of the second oil trough portion 68 so as to project to the left. The fitting projection 68a is fitted to the fitting hole formed in the partition wall part 29B of the left crankcase 7. Further, in the oil gutter 66, the connecting part between the first oil gutter part oil 67 and the second oil trough part 68 is provided with an extension part 68E extending backwards.

An adjustment projection 68b having the same shape as that of the adjustment projection 68a is provided in the extension part 68E so as to project to the left, and the adjustment projection 68b is fitted to the hole. fit formed in partition wall portion 29B. Through the fitting projection 68a and the fitting projection 68b, the oil gutter 66 is attached to the partition wall part 29B of the left crankcase 7 at the front and rear sides of the duct part 68D.

In other words, the oil trough 66 is attached to the transmission case 5 in such a way that the oil supply parts 69F and 69G are inserted into the lubricating grooves and the fitting projections 68a and 68b are inserted into the adjustment holes and separation (the rightward movement of the oil trough 66) is prevented such that a projecting part which projects forward from the side wall 67B contacts the transmission housing 5.

Hereinafter, an operation is described.

As indicated by a dotted arrow in Fig. 4 corresponding to a left side view, when the vehicle 1 is moving forward, in the gear reducer mechanism 33, the input shaft 34 rotates counterclockwise, the first intermediate shaft 35 rotates in the clockwise direction of rotation, and the second intermediate shaft 36 rotates in the counterclockwise direction of rotation. In the speed change mechanism 40, the input shaft 11 rotates counterclockwise and the forward output shaft 12 rotates clockwise. As a result, the final driven gear 15A rotates counterclockwise.

The lubricating oil supplied from the oil pump 47 to the oil conduit 48 through the oil discharge passage 44a is discharged from the front end portion of the oil conduit 48 disposed at the upper part of the housing chamber of the speed reducer mechanism 30B. This lubricating oil collides with the ribs 27b and 28d of the cover 27 so that its flow speed decreases, is dispersed inside the housing chamber of the speed reducer mechanism 30B, flows down up to each pinion of the gear reducer mechanism 33 and is picked up by the oil gutter 60 provided under the ribs 27b and 28d.

As illustrated in Fig. 10, the lubricating oil caught by the oil trough 60 flows through the oil trough 60 and flows from the oil outlet 60A. The lubricating oil flowing from the oil outlet 60A is guided to the placement part 29H and the guide groove 29g and is introduced into the oil circulation space 53A.

Lubricating oil O1 introduced into the oil circulation space 53A is supplied to the oil seal 55, passes through the ball bearing 51A to lubricate the ball bearing 51A, and is discharged from the oil circulation space 53A.

As illustrated in Fig. 8, the lubricating oil O1 discharged from the oil circulation space 53A flows downward while lubricating the meshing portion between the first drive gear 34A and the first driven gear 35A arranged on the lateral side from the lower part of the oil circulation space 53A and is guided to the oil circulation space 53C from the bearing holding part 29E along the concave part 29M as indicated by the lubricating oil O2 in Fig. 7 and 8.

As illustrated in Fig. 8, the lubricating oil O2 introduced into the oil circulation space 53C lubricates the needle bearing 51C, the outer peripheral surface of the first intermediate shaft 35 corresponding to the rolling surface of the needle bearing 51C and the surface of inner diameter of the bearing holding part 29E and flows downward from the oil circulation space 53C.

As illustrated in Fig. 10, the lubricating oil caught by the oil trough 60 is guided from the oil outlet 60B to the guide groove 27g and is introduced into the oil circulation space 53B as indicated by the O3 lubricating oil. Part of the lubricating oil O3 introduced into the oil circulation space 53B passes through the ball bearing 51B, lubricates the ball bearing 51B, and is discharged downward from the oil circulation space 53B.

As illustrated in Fig. 8, the lubricating oil O3 discharged downward from the oil circulation space 53B lubricates the meshing portion between the first driving gear 34A and the first driven gear 35A disposed on the lateral side of the lower part of the oil circulation space 53B.

Meanwhile, part of the lubricating oil introduced into the oil circulation space 53B is introduced from the oil circulation space 53B into the oil circulation space 53D via the oil passage 27d as indicated by lubricating oil O4 in Fig. 11.

The lubricating oil O4 guided in the oil circulation space 53D is introduced from the oil circulation space 53D into the oil passage 35a of the first intermediate shaft 35 via the conduit part 61B of guide plate 61 as indicated by lubricating oil O5 in Fig. 8.

The lubricating oil O5 introduced into the oil passage 35a is introduced into the oil circulation space 53C of the bearing holding part 29E, lubricates the needle bearing 51C provided in the bearing holding part 29E , and is forced downward from the oil circulation space 53C.

Part of the lubricating oil O5 introduced into the oil passage 35a is supplied from a gap between the conduit portion 61B and the inner peripheral surface of the first intermediate shaft 35 to the ball bearing 51D (see O6 lubricating oil in Fig. 9). As a result, the 51D ball bearing is lubricated.

As illustrated in Fig. 9, the lubricating oil O6 having lubricated the ball bearing 51D is discharged downward from the oil circulation space 53D. The meshing part between the second driven gear 36A and the second driving gear 35B is located on the lateral side of the lower part of the bearing holding part 27D.

Accordingly, the meshing part between the second driven gear 36A and the second driving gear 35B is lubricated by the lubricating oil O6 discharged from the bearing holding part 27D.

In the oil gutter 60 of this embodiment, since the opening width of the oil outlet 60B is wider than the opening width of the oil outlet 60A, a large amount of the oil Lubrication can be supplied from the oil circulation space 53B of the bearing holding portion 27C. Then, a large amount of lubricating oil flows through the oil passage 27d so that a large amount of lubricating oil can be supplied to the oil circulation space 53D.

For this reason, a sufficient amount of oil can be supplied from the oil passage 27d to the ball bearing 51D supporting the left end portion of the first intermediate shaft 35. In addition, a sufficient amount of lubricating oil can also be supplied to the needle roller bearing 51C provided in a small gap between the right end portion of the first intermediate shaft 35 and the bearing holding portion 29E and provided on the side opposite to the first intermediate shaft 35 so as to be separated between them, by means of the oil passage 35a of the first intermediate shaft 35.

Meanwhile, the lubricating oil O stored in the bottom part of the left crankcase 7 is scraped by the final driven gear 15A and is introduced from the oil introducing part 67D of the first oil trough part 67 into the first oil passage 70 as indicated by lubricating oil O7 in Fig.5.

The lubricating oil O7 introduced into the first oil passage 70 is guided from the first oil passage 70 to the third oil passage 72 via the second oil passage 71.

As illustrated in Fig. 9, the cylindrical duct part 68D is provided in the side wall 68C of the second oil gutter part 68 constituting the second oil passage 71, and the duct part 68D passes through the oil circulation space 53E and is inserted into the oil passage 36a of the second intermediate shaft 36.

Consequently, as illustrated in Fig. 9, the lubricating oil O7 flowing through the second oil passage 71 is supplied to the oil passage 36a of the second intermediate shaft 36 via the conduit portion 68D as indicated by the oil of O8 lubrication.

Part of the lubricating oil O8 supplied to the oil passage 36a is discharged from the oil passage 36a to the oil circulation space 53E as indicated by the lubricating oil O9, lubricates the bearing at 51E balls provided in the bearing holding part 29F, and is pushed back from the oil circulation space 53E.

The lubricating oil O9 discharged downward from the oil circulation space 53E flows along the pinion housing part 29G and lubricates the meshing part between the third driving pinion 36B and the 17D fourth gear output.

The lubricating oil O8 flowing through the oil passage 36a is introduced into the oil circulation space 53F as indicated by the lubricating oil O10. After the lubricating oil O10 introduced into the oil circulation space 53F lubricates the ball bearing 51F, the lubricating oil is discharged from the oil circulation space 53F.

Meanwhile, the side walls 69B and 69C of the third oil trough portion 69 of the oil trough 66 are respectively provided with the oil receivers 69D and 69E provided to extend upward from the walls side 69B and 69C.

As illustrated in Fig. 4, the peripheral wall portion 28 is disposed in front of the input shaft 34 and the first intermediate shaft 35 and receives the dispersed lubricating oil in accordance with the rotation of the gear. The oil receiver 69D is provided under the peripheral wall portion 28, and the oil receiver 69D receives lubricating oil O11 dispersed from the first drive gear 34A, the first driven gear 35A and the second drive gear 35B of the speed reducing mechanism 33 and flowing down along the peripheral wall portion 28 and guides the lubricating oil to the third oil passage 72.

The oil receiver 69E is provided on the side of the second countershaft 36 with respect to the oil receiver 69D and is inclined from the side wall 69C toward the speed reduction mechanism 33. Further, the second drive gear 35B and the second driven gear 36A rotate in a direction in which their meshing position approaches the upper end of the oil receiver 69E.

Accordingly, the oil receiver 69E receives lubricating oil O12 dispersed from the meshing portion between the second driving gear 35B and the second driven gear 36A and guides the lubricating oil to the third passage of oil 72.

The lubricating oil flowing through the third oil passage 72 is supplied from the oil supply part 69F provided at the left end part of the third oil trough part 69 to to the ball bearing 50A provided in the input shaft 11. Accordingly, the ball bearing 50A is lubricated with oil.

Further, the lubricating oil flowing through the third oil passage 72 is supplied from the oil supply part 69G provided at the left end part of the third oil trough part. 69 to ball bearing 50B provided in forward output output shaft 12.

As a result, the 50B ball bearing is oil lubricated. The third oil passage 72 is provided with notches 69b and 69c, and the lubricating oil flowing from the notches 69b and 69c is supplied to the synchronization device or the pinion arranged below and the meshing part of the pinion .

The lubricating oil discharged from the oil troughs 60 and 66 finally returns to the bottom part of the left crankcase 7 and joins the lubricating oil O stored in the bottom part of the left crankcase 7.

As described above, according to the driving device 4 of this embodiment, the oil circulation spaces 53A to 53F through which the lubricating oil circulates are formed inside the transmission case 5 and bearing holding cylindrical parts 27C, 27D, 27E, 29D, 29E and 29F movably supporting in rotation the input shaft 34, the first intermediate shaft 35 and the second intermediate shaft 36 via the intermediate bearings balls 51A, 51B, 51D, 51E and 51F and needle bearing 51C are provided therein.

The input shaft 34, the first intermediate shaft 35 and the second intermediate shaft 36 are provided so as to be separated from each other in the up-down direction so that the speed reducer mechanism 33 projects upward from relative to the shift mechanism 40 and the transmission case 5 includes the oil trough 66 which catches the lubricating oil scraped by the final driven gear 15A and supplies the lubricating oil to the shift mechanism 40.

The oil gutter 66 is provided at the lower part of the speed reduction mechanism 33 so as to catch the lubricating oil dispersed from the speed reduction mechanism 33 and flowing down and includes the conduit part 68D capable of supplying oil to the oil circulation space 53E of the bearing holding part 29F supporting the second intermediate shaft 36 located at the lowest position and to the oil circulation space 53F of the bearing holding part 27E.

Accordingly, the oil gutter 66 can catch the lubricating oil scattered from the speed reduction mechanism 33 and flowing downward in addition to the lubricating oil scraped by the final driven gear 15A and can increase the amount of lubricating oil received by the oil trough 66. For this reason, the amount of lubricating oil flowing to the oil trough 66 per unit time can be increased.

Thus, a sufficient amount of lubricating oil can be supplied to the oil circulation spaces 53E and 53F of the bearing holding portions 27E and 29F and the ball bearings 51E and 51F can be lubricated. For this reason, the durability of 51E and 51F ball bearings can be improved.

In addition, a sufficient amount of lubricating oil can be supplied to the second synchronizing device 19, the third synchronizing device 20, the meshing portion between the input gear 16D and the output gear 17D, and the meshing part between the input pinion 16E and the output pinion 17E. For this reason, the durability of the second synchronization device 19 and the like can be improved by lubricating the second synchronization device 19 and the like.

Thus, the driving device 4 of this embodiment can improve the lubricating performance of the speed change mechanism 40 and the speed reducer mechanism 33 by increasing the amount of lubricating oil supplied to the speed change mechanism. gear 40 and the gear reducer mechanism 33 and improve the reliability of the gear change mechanism 40 and the gear reducer mechanism 33.

Further, according to the drive device 4 of this embodiment, the oil gutter 66 is provided at the same height position as that of the second intermediate shaft 36 located at the lowest position of the speed reducer mechanism 33. and conduit portion 68D supplies lubricating oil to oil passage 36a passing through the axis of second countershaft 36.

Accordingly, lubricating oil can be supplied to the ball bearing 51F provided at the left end portion of the second intermediate shaft 36 in addition to the ball bearing 51E provided at the right end portion of the second intermediate shaft 36 so that the two ball bearings 51E and 51F can be lubricated.

Further, according to the drive device 4 of this embodiment, the oil gutter 66 includes oil receivers 69D and 69E which catch lubricating oil dispersed and flowing down from the reduction gear. speed 33.

Accordingly, a large amount of the lubricating oil scattered from the speed reduction mechanism 33 and flowing downward may be caught by the oil receivers 69D and 69E and a large amount of the lubricating oil may be picked up by the oil gutter 66. Accordingly, it is possible to further increase the amount of the lubricating oil supplied to the speed change mechanism 40 and the speed reducer mechanism 33 and to more effectively improve the lubricating performance of gear shift mechanism 40 and gear reducer mechanism 33.

Further, the oil receivers 69D and 69E are provided in the third oil gutter part 69 on the downstream side of the duct part 68D.

Accordingly, even when the lubricating oil is supplied (consumed) from the duct portion 68D on the upstream side of the third oil trough portion 69 to the oil passage 36a of the second intermediate shaft 36, a large amount of lubricating oil can be introduced into the third oil passage 72 of the third oil trough part 69 through the oil receivers 69D and 69E.

For this reason, a sufficient amount of lubricating oil can be supplied from the third oil passage 72 to the second synchronization device 19 and the like by means of the notches 69b and 69c and the lubricating performance of the shift mechanism 40 can be improved more effectively. Further, a sufficient amount of lubricating oil can be supplied to the ball bearings 50A and 50B by means of the oil supply portions 69F and 69G. Further, the lubricating oil can also be supplied to the conduit part 68D and the lubricating oil can be supplied from the conduit part 68D to the oil passage 36a.

Here, the downstream side is the downstream side in the flow direction of the lubricating oil when the lubricating oil scraped by the final driven gear 15A flows in order in the first oil passage 70, the second oil passage 71 and the third oil passage 72.

Further, according to the drive device 4 of this embodiment, the transmission case 5 includes the peripheral wall portion 28 surrounding the speed reducer mechanism 33. Further, the oil receiver 69D is provided under the portion. peripheral wall portion 28 and catches the lubricating oil dispersed from the speed reduction mechanism 33 and flowing down along the peripheral wall portion 28.

Accordingly, the lubricating oil flowing down along the peripheral wall portion 28 can be effectively caught by the oil receiver 69D, and a large amount of the lubricating oil can be caught by the gutter. oil 66. Accordingly, it is possible to further increase the amount of the lubricating oil supplied to the speed change mechanism 40 and the speed reduction mechanism 33 and to improve the lubricating performance of the mechanism more effectively. shifter 40 and gear reducer mechanism 33.

Further, according to the drive device 4 of this embodiment, the oil receiver 69E is inclined from the side wall 69C of the oil trough 66 toward the meshing portion between the second drive gear 35B and the second driven gear 36A.

Accordingly, the lubricating oil dispersed from the second drive gear 35B and the second driven gear 36A can be effectively caught by the oil receiver 69E, and a large amount of the lubricating oil can be caught by the drain channel. oil 66. Accordingly, it is possible to further increase the amount of the lubricating oil supplied to the shift mechanism 40 and the speed reducer mechanism 33 and to improve the lubricating performance of the shift mechanism more effectively. gear 40 and gear reducer mechanism 33.

Further, in the driving device 4 of this embodiment, the lubricating oil is supplied to the upper part of the speed reducing mechanism 33 through the oil conduit 48, but this invention is not limited thereto. . For example, an oil passage can be formed in the cover 27 or the left crankcase 7 so that the lubricating oil discharged from the oil pump 47 is supplied to the upper part of the speed reducer mechanism 33 through the oil passage.

Further, in the drive device 4 of this embodiment, the bearing is configured as the ball bearing or the needle bearing, but is not limited to the ball bearing.

Although embodiments of this invention have been described, it is apparent that one skilled in the art could have made changes without departing from the scope of this invention. All such modifications and equivalents are intended to be covered in the appended claims.

1 Vehicle,
4 Drive device (hybrid vehicle drive device),
5 Transmission housing,
8 Heat engine (internal combustion engine),
11 Input shaft (shift mechanism),
12 Forward output shaft (shift mechanism),
15 Differential device,
15A Final driven pinion (pinion element),
16A, 16B, 16C, 16D, 16E, 16F Input gear (shift mechanism),
17A, 17B, 17C, 17D, 17E, 17F Output gear (shift mechanism),
27C, 27D Bearing retainer (upper bearing retainer),
27E Bearing retainer part (lower bearing retainer part),
28 Part of peripheral wall,
29D, 29E Bearing retainer part (upper bearing retainer part),
29F Bearing retainer part (lower bearing retainer part),
32 Electric motor,
33 Speed reduction mechanism,
34 Input shaft (rotating shaft),
35 First intermediate shaft (rotating shaft),
36 Second intermediate shaft (rotating shaft),
37 First gear reduction gear set (gear reduction gear set),
38 Second gear reduction gear set (gear reduction gear set),
39 Third gear reduction gear set (gear reduction gear set),
40 gear shift mechanism,
40L, 40R Drive wheel,
51A, 51B, 51D, 51E, 51F Ball bearing (bearing),
51C Needle bearing (bearing),
53A, 53B, 53C, 53D, 53E, 53F Oil circulation space,
66 Oil gutter,
68D Duct part (oil supply part),
69C Side wall (oil gutter side wall),
69D Oil receiver (first oil receiver),
69E Oil receiver (second oil receiver).

Claims (5)

Lubrication structure of a hybrid vehicle drive device (4) comprising:
a speed change mechanism (11) changing the power transmitted from an internal combustion engine (8);
a differential device comprising a pinion member (15A) receiving power from the shifting mechanism (11) and transmitting power from the shifting mechanism (11) to the left and right driving wheels;
a speed reduction mechanism comprising a plurality of rotary shafts (34) and a plurality of sets of speed reduction gears (37) provided in the plurality of rotary shafts (34) and transmitting a rotation of a motor to the mechanism shifting gear (11) by reducing the rotation, the plurality of rotating shafts (34) being arranged to be separated from each other in an up-down direction so that the gear reduction mechanism protrudes upwardly from to the gear change mechanism (11);
a transmission case storing lubricating oil in a bottom part and housing the gear change mechanism (11), the gear reduction mechanism and the differential device; and
an oil gutter capturing lubricating oil scraped off by the pinion member (15A) and supplying the lubricating oil to the gear change mechanism (11),
wherein the transmission case comprises a plurality of bearing retaining portions (51A, 51B, 51D, 51E, 51F) having an oil circulation space formed therein such that lubricating oil flows therein and supports rotatably the plurality of rotary shafts (34) via a bearing (51A, 51B, 51D, 51E, 51F),
wherein the bearing holding portions (51A, 51B, 51D, 51E, 51F) of the plurality of bearing holding portions (51A, 51B, 51D, 51E, 51F) include a lower bearing portion (27E) (51A, 51B, 51D, 51E, 51F) supporting the rotary shaft (34) located in the lowest position among the plurality of rotary shafts (34) and an upper part (27D) for holding the bearing (51A, 51B) , 51D, 51E, 51F) located above the lower part (27E) for retaining the bearing (51A, 51B, 51D, 51E, 51F),
wherein the oil gutter is provided at a lower part of the speed reducing mechanism so as to capture lubricating oil dispersed from the speed reducing mechanism and flowing downward, and
wherein the oil gutter comprises an oil supply part (68D) supplying lubricating oil to the oil circulation space of the lower bearing holding part (27E) (51A, 51B, 51D, 51E, 51F). A lubricating structure of the hybrid vehicle drive device (4) according to claim 1,
wherein the oil gutter is provided at the same height position as that of the rotary shaft (34) supported by the lower bearing retaining portion (27E) (51A, 51B, 51D, 51E, 51F), and
wherein the oil supply portion (68D) supplies lubricating oil to an axis of the rotary shaft (34) supported by the lower bearing holding portion (27E) (51A, 51B, 51D, 51E) , 51F). A lubricating structure of the hybrid vehicle drive device (4) according to claim 1 or 2,
wherein the oil gutter comprises an oil receiver picking up lubricating oil dispersed from the speed reduction mechanism and flowing downward. A lubricating structure of the hybrid vehicle drive device (4) according to claim 3,
wherein the transmission case includes a peripheral wall portion surrounding the speed reduction mechanism, and
the oil receiver being provided under the peripheral wall portion and collects lubricating oil dispersed from the speed reducing mechanism and flowing downwardly along the peripheral wall portion. A lubricating structure of the hybrid vehicle drive device (4) according to claim 4,
wherein the oil receiver is a first oil receiver (69D), the oil gutter comprises a second oil receiver (69E) different from the first oil receiver (69D), and
the second oil receiver (69E) being inclined from a side wall of the oil gutter towards the speed reduction mechanism.