JP2001032915A - Lubricating structure of power transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a lubricating structure capable of feeding lubricating oil to the side of a bearing even at the time of tracting a vehicle. SOLUTION: An oil passage 52 to feed lubricating oil scraped up by a ring gear rotating by motive power input from a wheel to the side of bearings 39, 40 is provided on an outer peripheral side of a counter drive gear 37 in a casing 4 in a lubricating structure of a motive power transmission having the counter drive gear 37 arranged free to rotate around an axis X1 as its center in the inside of the easing 4 and connected to an engine and the wheel free to transmit motive power, the ring gear arranged free to rotate around a second axis in parallel with the axis X1 as its center and connected to the counter drive gear 37 and the wheel free to transmit motive power, the bearings 39, 40 to hold the counter drive gear 37 free to rotate and lubricating oil stored in the inside of the easing 4.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION The present invention relates to a rotating member connected to a driving force source and wheels of a vehicle so as to be capable of transmitting power, and lubricating oil is contained in the casing. The lubrication structure being used.

[0002]

2. Description of the Related Art A power transmission device is disposed on an output side of a driving force source of a vehicle. A transmission that forms a part of the power transmission device includes a rotating shaft such as an input shaft and an output shaft, and an input shaft. It has a gear transmission mechanism arranged between the shaft and the output shaft. Then, the torque input to the input shaft is transmitted to the output shaft via the gear transmission. Thus, the transmission is provided with various rotating members, and the torque is transmitted by these rotating members. By the way, since these rotating members are rotatably held by the bearings, there is a possibility that heat generation, wear, seizure, etc. may occur in the components of the bearings as the rotation speed of the rotating members increases.

An example of a device for lubricating bearings provided in a transmission is disclosed in Japanese Patent Application Laid-Open No. Hei 10-299875 and a collection of automotive technology examples (issue number 93444, Japan Automotive Industry Association Intellectual Property Section, 1993. 5.10). Japanese Patent Application Laid-Open No. 10-299875
In this publication, a bearing is attached to a case partition of an automatic transmission, and the bearing holds a counter gear rotatably. This counter gear is formed in a cylindrical shape, and a plurality of first oil grooves penetrating the counter gear in the radial direction are formed in the circumferential direction.

[0004] The bearing has an inner ring and an outer ring, the outer ring is fixed to the case partition, and the inner ring is fixed to the outer periphery of the counter gear. A plurality of tapered rollers are provided between the inner ring and the outer ring. Further, a plurality of second oil grooves penetrating the inner ring in the radial direction are formed in the circumferential direction.

In the above configuration, the power of the driving force source is transmitted to the counter gear to rotate the counter gear, and the torque is transmitted to the wheels so that the vehicle runs. Also, during operation of the driving force source, the oil pump is driven by the power to pump up the oil, and this oil passes through the first oil groove and the second oil groove to form an inner ring and an outer ring of the bearing. Supplied during. In this way, the bearing is lubricated and cooled.

On the other hand, in the lubricating device described in the automobile technology casebook, a counter gear is held in a casing via two bearings, and a lubricating hole is formed at a position corresponding to between the bearings of the counter gear. Have been. The lubricating oil is guided from the shaft center side to the bearing side via the lubrication hole.

[0007]

When a faulty vehicle is towed, the power of the driving force source is not transmitted to the input shaft, whereas the power input from the wheels is transmitted via the counter shaft. It is transmitted to the input shaft. Therefore, even when the vehicle is towed,
As with running vehicles, there is a need to lubricate and cool the bearings.

[0008] However, when the vehicle is towed, the driving force source is stopped, so that the oil pump having a function of supplying oil to the bearings is also stopped. Therefore, in the lubricating structure described in the above-mentioned Japanese Patent Application Laid-Open No. 10-299875 and the collection of automobile technology, the bearing cannot be lubricated and cooled by oil when the vehicle is towed, and the heat generation, wear, Seizure could occur.

The present invention has been made in view of the above circumstances, and has as its object to provide a lubricating structure that can lubricate and cool a bearing even when the vehicle is being towed.

[0010]

In order to achieve the above object, an invention according to claim 1 is provided so as to be rotatable about a first axis inside a casing, and to provide a driving force source and wheels. A first rotating member connected to the first rotating member so as to be capable of transmitting power to the first rotating member and a wheel rotatably around a second axis parallel to the first axis, and capable of transmitting power to the first rotating member and the wheels; A lubricating structure of a power transmission device having a second rotating member connected to the first rotating member, a bearing rotatably holding the first rotating member, and a lubricating oil housed inside the casing. An oil passage for supplying lubricating oil scooped up by the second rotating member, which is rotated by power input from the wheel, to the bearing side is provided on an outer peripheral side of the one rotating member. It is an.

According to the first aspect of the invention, when the power of the wheels is input to the second rotating member when the vehicle is towed, and the second rotating member rotates, the lubricating oil is scraped up and the inside of the casing is centrifugally exerted. Will be skipped. Here, since the first axis and the second axis are arranged in parallel, the lubricating oil blown out by the centrifugal force easily reaches the outer peripheral side of the first rotating member. To the bearing side.

According to a second aspect of the present invention, in addition to the configuration of the first aspect, a snap ring is provided on the casing to prevent the bearing from moving in the axial direction of the first rotating member. Is characterized in that a cut is formed in a part in the circumferential direction, and an opening on the bearing side in the oil passage is arranged facing the cut.

According to the second aspect of the present invention, in addition to the same effect as that of the first aspect of the present invention, since the opening of the oil passage on the bearing side is arranged facing the cut of the snap ring, When the lubricating oil is sent to the bearing side through the oil passage, the lubricating oil flows smoothly without being hindered by the snap ring.

According to a third aspect of the present invention, in addition to the configuration of the first or second aspect, the height of the lower end of the first rotating member inside the casing is higher than the height of the second rotating member inside the casing. And the liquid level of the lubricating oil is set so as not to contact the first rotating member and to contact the second rotating member. It is characterized by the following.

According to the third aspect of the present invention, the same operation as the first or second aspect of the present invention is produced, and even if the lubricating oil cannot be blown to the bearing side by the rotation of the first rotating member, the second operation can be performed. The lubricating oil is blown off by the rotation of the rotating member, and the lubricating oil is sent to the oil passage.

According to a fourth aspect of the present invention, there is provided a rotating member rotatably disposed inside a casing and connected to a driving force source and wheels so as to transmit power, and rotatably holds the rotating member. In the lubrication structure of the power transmission device having a bearing and a lubricating oil housed inside the casing, the casing includes a lubricating oil in which the rotating member is rotated by the power input from the wheels and is blown off. An oil passage for supplying to the bearing side is provided.

According to the fourth aspect of the present invention, the lubricating oil that has been rotated and sputtered by the power input from the wheels is sent to the bearing by the oil passage, and the bearing is lubricated and cooled.

[0018]

Next, the present invention will be specifically described with reference to the drawings. FIG. 2 is a skeleton diagram of one embodiment in which the present invention is applied to an FF vehicle (vehicle with front-wheel drive with an engine). In FIG. 2, reference numeral 1 denotes an engine as a driving force source of a vehicle. As the engine 1, an internal combustion engine, specifically, a gasoline engine, a diesel engine, an LPG engine, or the like is used. The crankshaft 2 of the engine 1 is arranged in the width direction of the vehicle.

On the output side of the engine 1, a transaxle 3 is provided. The transaxle 3 has a hollow casing 4 inside, and a torque converter 5, a speed change mechanism 6, and a final reduction gear (in other words, a differential device) 7 are provided in an internal space D1 of the casing 4. First, the configuration of the torque converter 5 will be described. An input shaft 8 rotatable about the same axis X1 as the crankshaft 2 is provided in the internal space D1 of the casing 4.
The turbine runner 9 is attached to an end of the engine 1 on the engine 1 side.

On the other hand, a front cover 11 is connected to a rear end of the crankshaft 2 via a drive plate 10, and the front cover 11 is connected to a pump impeller 12.
Is connected. The turbine runner 9 and the pump impeller 12 are arranged to face each other, and a stator 13 is provided inside the turbine runner 9 and the pump impeller 12. Further, a lock-up clutch 14 is provided between the front cover 11 and the turbine runner 9.
A casing 15 is formed by the front cover 11 and the pump impeller 12 configured as described above, and the inside of the casing 15 is supplied with oil as a working fluid.

With the above configuration, the power (torque) of the engine 1 is transmitted from the crankshaft 2 to the front cover 11. At this time, when the lock-up clutch 14 is released, the torque of the pump impeller 12 is transmitted to the turbine runner 9 by the fluid, and then transmitted to the input shaft 8. The torque transmitted from the pump impeller 12 to the turbine runner 9 is
Amplified by On the other hand, when the lock-up clutch 14 is engaged, the torque of the front cover 11 is mechanically transmitted to the input shaft 8.

An oil pump 16 is provided between the torque converter 5 and the speed change mechanism 6 in the internal space D1 of the casing 4. The rotor 17 of the oil pump 16 and the pump impeller 12 are cylindrical hub 1
8. The body 19 of the oil pump 16 is fixed to the casing 4 side. Therefore, the oil pump 16 can be driven by the power of the engine 1 to pump oil from an oil pan (not shown).

On the other hand, the speed change mechanism 6 has a first planetary gear mechanism 20 and a second planetary gear mechanism 21, and the first planetary gear mechanism 20 and the second planetary gear mechanism 21 are arranged around the input shaft 8. Are located in The first planetary gear mechanism 20 includes a sun gear 23, a ring gear 24 that is an internal gear disposed concentrically with the sun gear 23,
This is a single pinion type planetary gear mechanism in which a carrier 26 holding a plurality of pinion gears 25 meshed with a sun gear 23 and a ring gear 24 has three rotating elements.
A first hollow shaft 27 that is rotatable relative to the input shaft 8 is attached to an outer periphery of the input shaft 8, and a sun gear 23 is formed at one longitudinal end of the first hollow shaft 27. An end of the first hollow shaft 27 on the oil pump 16 side is supported by a thrust bearing 61A. With this thrust bearing 61A, the first
The movement of the hollow shaft 27 in the axial direction toward the oil pump is restricted. Further, the first hollow shaft 27
Is provided in the radial direction.

The second planetary gear mechanism 21 includes a sun gear 28, a ring gear 29 which is an internal gear disposed concentrically with the sun gear 28, and a plurality of pinion gears 30 meshed with the sun gear 28 and the ring gear 29. This is a single pinion type planetary gear mechanism using the held carrier 31 and three rotating elements. A second hollow shaft 32 that is rotatable relative to the input shaft 8 is attached to the outer periphery of the input shaft 8, and a carrier 31 is connected to one end of the second hollow shaft 32 in the longitudinal direction. Further, a third hollow shaft 63 is attached to the outer periphery of the second hollow shaft 32 so as to be relatively rotatable. And
The sun gear 28 is formed on the outer periphery of the third hollow shaft 63.

Further, the carrier 31 and the ring gear 24 are connected by a cylindrical connecting drum 33 so as to be integrally rotatable. In addition, the carrier 26 and the ring gear 29 are connected by a connecting drum 34A so as to be integrally rotatable. Further, a connecting drum 34 that is rotatable relative to the first hollow shaft 27 is attached to the outer periphery of the first hollow shaft 27. An end of the connecting drum 34 opposite to the oil pump 16 is supported by a thrust bearing 34B. The axial movement of the connecting drum 34 away from the oil pump 16 is restricted by the thrust bearing 34B.

A cylindrical member 35 having a substantially L-shaped cross section in the radial direction is spline-fitted to the outer periphery of the connecting drum 34. The cylindrical member 35 has a cylindrical portion 43 and an outward flange 36, and a counter drive gear 37 is formed on the outer periphery of the outward flange 36. The counter drive gear 37 is constituted by a so-called helical gear. A nut 34A is fastened and fixed to the end of the cylindrical portion 43, and the nut 34A regulates movement of the cylindrical member 35 in the axial direction toward the right direction (the oil pump 16 side) in FIG. Have been. Each gear constituting the first planetary gear mechanism 20 is also constituted by a helical gear, and each gear constituting the second planetary gear mechanism 21 is also constituted by a helical gear. As described above, the transmission mechanism 6 has various rotating elements.

On the other hand, a projecting wall 38 is formed inside the casing 4 as shown in FIG. This protruding wall 38
Project from the inner surface of the casing 4 toward the axis X1. Bearings (specifically, tapered roller bearings) 39 and 40 are attached to the inner periphery of the protruding wall 38. Bearing 3
The outer diameters of the bearings 39 and 40 are set smaller than the outer diameter of the counter drive gear 37. One of the bearings 39 has an inner ring 41 and an outer ring 42, and a plurality of tapered rollers 43 as rolling elements disposed between the inner ring 41 and the outer ring 42 in the circumferential direction.
Then, the inner ring 41 is fitted and fixed to the outer periphery of the cylindrical portion 43,
One end surface 44 of the inner ring 41 is connected to the connecting drum 3
4 is in contact with the outward flange 45. In addition, outer ring 4
The second inner peripheral surface 42A is provided with a taper in a direction in which the diameter increases as the distance from the bearing 40 increases.

The other bearing 40 includes an inner ring 46 and an outer ring 4.
7 and a plurality of tapered rollers 48 as a plurality of rolling elements arranged in the circumferential direction between the inner ring 46 and the outer ring 47. The inner ring 46 is fitted and fixed to the outer periphery of the cylindrical portion 43, and one end surface 49 of the inner ring 43 is in contact with the outward flange 36. The bearing 3 is provided on the inner peripheral surface 47A of the outer ring 47.
The taper in the direction in which the diameter increases as the distance from the nozzle 9 increases. Thus, the bearing 39 and the bearing 40 are mutually plane-symmetric. The above two bearings 39, 40
Is a radial bearing that rotatably holds the connecting drums 34, 35, the first hollow shaft 27, and the input shaft 8.

A snap ring mounting groove 50 is formed on the inner periphery of the protruding wall 38, and a snap ring 51 is mounted in the snap ring mounting groove 50. The snap ring 51 is disposed between the bearing 39 and the bearing 40. This snap ring 51
Is substantially C in which the abutment 51A is formed in a part of the circumferential direction.
It is configured in a character shape. That is, the snap ring 51
A gap is formed between both ends 54 and 55 facing the abutment 51A.

The snap ring 51 thus configured
Are in contact with the end surface 42A of the outer race 42 of the bearing 39 and the end surface 47A of the outer race 47 of the bearing 40. This end face 42A
And the end face 47A are opposed to each other. In this way, a gap corresponding to the thickness of the snap ring 51 is formed between the bearing 39 and the bearing 40 in the axial direction of the input shaft 8.

Further, the projecting wall 38 is formed with an oil passage 52 connecting the side face of the projecting wall 38 on the counter drive gear 37 side and the snap ring mounting groove 50. The inlet 54 on the counter gear 37 side in the oil passage 52 is
It is arranged on the outer peripheral side of the outlet 53. The outlet 53 on the snap ring mounting groove 50 side in the oil passage 52
Are formed facing the abutment 51A. In other words, in the circumferential direction of the snap ring attachment groove 51, the phase of the outlet 53 matches the phase of the abutment 51A.
The entirety of the oil passage 52 is connected to the input shaft 8.
(In other words, it is disposed above the rotation center A1 of the counter drive gear 37).

On the other hand, the cylindrical member 35 has a cylindrical portion 43
Are formed in the radial direction. The connecting drum 34 has an oil passage 57 penetrating through the cylindrical portion 56 in the radial direction. Further, an oil passage 58 in the axial direction is formed inside the input shaft 8. A part of the oil pumped by the oil pump 16 is supplied to the oil passage 58. Also,
The input shaft 8 is provided with an oil passage 59 penetrating from the outer peripheral surface thereof toward the oil passage 58.

Next, a description will be given of a friction engagement device such as a clutch or a brake for switching the torque transmission path of the transmission mechanism 6. First, the input shaft 8 and the first
A first clutch C1 for controlling a torque transmission state with the hollow shaft 27 is provided. This first clutch C
1 has a cylindrical clutch hub 60 as shown in FIG. 1, and an inner periphery of the clutch hub 60 and an outward flange 61 of the first hollow shaft 27 are joined. Also,
A hole 61 is formed in the clutch hub 60 so as to penetrate in the axial direction.

The oil passage 58 and the bearings 39 and 40 communicate with each other via the oil passages 59, 27A, 57, and 55 so that the liquid can flow therethrough. The outward flange 36 has a hole 36A penetrating in the axial direction. By the hole 36A, the space between the clutch hub 60 and the outward flange 36 and the space in which the bearings 39 and 40 are arranged communicate with each other so that the liquid can flow.

On the other hand, a second clutch C2 for controlling a torque transmission state between the input shaft 8 and the second hollow shaft 32 is provided. Also, the input shaft 8
A third clutch C3 for controlling a torque transmission state between the third clutch C3 and the third hollow shaft 63 is provided. That is, the second clutch C2 and the third clutch C3 are arranged in parallel with each other. Further, a first brake B1 and a second brake are arranged between the sun gear 28 and the casing 4 in parallel with each other. Further, a first one-way clutch F1 is provided between the second brake B2 and the sun gear 28. A third brake B3 and a second one-way clutch F2 are arranged in parallel between the connecting drum 33 and the casing 4.

On the other hand, the countershaft 6 is rotatable about an axis Y1 parallel to the input shaft 8.
4 are provided. A counter driven gear 65 and a final drive gear 66 are formed on the counter shaft 64. The counter driven gear 65 and the counter drive gear 37 are meshed.
The final reduction gear 7 has a differential case 67 that can rotate about the axis Z1. The axis Z1 is
They are set parallel to the axes X1 and Y1. A ring gear 68 is formed on the outer periphery of the differential case 67, and the ring gear 68 and the final drive gear 66 are meshed.

Incidentally, the final drive gear 66
Are arranged closer to the engine 1 than the counter driven gear 65, and the final drive gear 66 is arranged as close to the counter driven gear 65 as possible. Therefore, the arrangement positions of the counter drive gear 37 and the counter driven gear 65 in the axial direction of the input shaft 8 and the arrangement positions of the final drive gear 66 and the ring gear 68 are as close as possible.

A plurality of pinion gears 68A are mounted inside the differential case 67, and two side gears 69 are engaged with the pinion gear 68A. A front drive shaft 70 is separately connected to the two side gears 69, and a front wheel 71 as a driving wheel is connected to each front drive shaft 70. The differential case 67 and the front drive shaft 70 are rotatably held by bearings (not shown) attached to the casing 4.

FIG. 4 is a schematic side sectional view of the casing 4. Comparing the arrangement positions of the input shaft 8 and the counter shaft 64, the input shaft 8 is arranged horizontally on the front side of the vehicle. And, behind the input shaft 8,
The counter shaft 64 is horizontally arranged at a position lower than the input shaft 8. That is, the rotation center A2 of the counter shaft 64 is higher than the rotation center A1 of the counter drive gear 37. Further, a ring gear 68 is disposed at a position rearward of the counter shaft 64 and lower than the input shaft 8. That is, the rotation center A of the ring gear 68
3 is located at a position lower than the rotation center A1. More specifically, the outer peripheral end (lower end) of the counter drive gear 37
Is located above the outer peripheral end (lower end) of the ring gear 68. A lubricating oil (oil) D2 is stored in the casing 4 on the bottom 4A side. This lubricating oil D
2, the ring gear 68 is immersed in the lubricating oil D2 to about half in the radial direction, while the counter drive gear 3
7 and the bearings 39 and 40 are set at positions not immersed in the lubricating oil D2.

On the other hand, an electronic control unit (not shown) for controlling the transmission mechanism 6 and the engine 1 and a hydraulic control unit (not shown) for controlling the transmission mechanism 6 and the lock-up clutch 15 are provided. This hydraulic control device
It comprises a solenoid valve for controlling the operation of the oil pump 16 and various clutches and brakes, and a hydraulic circuit. The running state of the vehicle (for example, vehicle speed and accelerator opening) is determined by the electronic control unit, and the hydraulic control unit is controlled based on the determination result, and various types of friction engagement devices such as clutches and brakes are engaged. When released, the speed ratio of the speed change mechanism 6 is controlled.

Here, the correspondence between the configuration of the embodiment and the configuration of the present invention will be described. The engine 1 corresponds to the driving force source of the present invention, and the cylindrical member 35 having the counter drive gear 37 is the present invention. The differential case 67 having the ring gear 68 corresponds to the first rotating member, the second rotating member of the present invention corresponds to the front wheel 71, the front wheel 71 corresponds to the wheel of the present invention, the outlet 53 corresponds to the opening of the present invention, and the axial line. X1 corresponds to the first axis of the present invention, axis Z1 corresponds to the second axis of the present invention, and abutment 51A corresponds to a break in the present invention.

The transmission mechanism 6 is a so-called stepped automatic transmission capable of setting four forward speeds and one reverse speed. In this transmission mechanism 6, engagement / disengagement control of frictional engagement devices such as various clutches and brakes performed when controlling the gear ratio is as shown in FIG. In FIG. 5, a mark “○” means that the friction engagement device is engaged, and a mark (○) indicates that engagement / release of the friction engagement device is irrelevant to transmission of power (in other words, torque). The symbol ◎ indicates that the vehicle is engaged in the coast state (in other words, the engine brake state), and the blank indicates that the friction engagement device is released.

In this way, various kinds of friction engagement devices are controlled, and the power (torque) of the engine 1 is transmitted to the counter shaft 64 via the input shaft 8 and the counter drive gear 37. The torque is transmitted to the wheels 71 via the final reduction gear 7, and the vehicle runs. During the rotation of the cylindrical member 35, the tapered rollers 43, 48 are formed in the bearings 39, 40.
Rolls along the inner and outer rings.

Further, since the counter drive gear 37 and the counter driven gear 65 are formed by helical gears, when torque is transmitted between the counter drive gear 37 and the counter driven gear 65,
An axial load (in other words, a thrust direction) acts on the counter driven gear 37. Specifically, a load that presses the cylindrical member 35 to the left in FIG. 1 acts. This load is applied to the snap ring 51 via the bearing 40.
, And this load is received by the snap ring 51. In this way, the movement of the bearing 40 in the axial direction is restricted.

Further, since each gear of the first planetary gear mechanism 20 is also formed of a helical gear, an axial load acts on the carrier 26 when transmitting torque. Specifically, a load that presses the connecting drum 34 rightward in FIG. 1 acts. This load is transmitted to the snap ring 51 via the bearing 39, and the load is received by the snap ring 51. In this way, the movement of the bearing 39 in the axial direction is restricted.

During the operation of the engine 1, the oil pump 16 is driven by the power, and the oil pumped from the oil pan is supplied to the oil passage 58 as lubricating oil. This lubricating oil is guided between the bearing 39 and the bearing 40 via the oil passages 59, 27A, 57, 55. Further, the lubricating oil passing through the hole 62 from the oil passage 59 is also supplied to the bearings 39 and 40 via the hole 36A. In this way, the bearings 39, 40 are forcibly lubricated and cooled by the lubricating oil sent by the drive of the oil pump 16, and heat generation, wear, and seizure of the bearings 39, 40 can be suppressed.

During the operation of the bearings 39 and 40 as described above, centrifugal force is generated in the inner ring 41 of the bearing 39 and the inner ring 46 of the bearing 40. Therefore, the lubricating oil supplied between the bearings 39 and 40 is separated from the inner ring 41 by the centrifugal force.
And the outer ring 42 and between the inner ring 46 and the outer ring 47. Therefore, the lubricating oil is evenly distributed between the inner ring 41 and the outer ring 42 and between the inner ring 46 and the outer ring 47, and the lubricating performance is further improved.

On the other hand, when the vehicle shown in FIG. 2 is towed, the power of the front wheels 71 is transmitted to the counter drive gear 37 via the final reduction gear 7 and the counter shaft 64, and the cylindrical member 35 rotates. Therefore, even when the vehicle is towed, the bearings 39 and 40 operate in the same manner as when the vehicle runs by the power of the engine 1. However, since the engine 1 is stopped when the vehicle is towed, the oil pump 16 is also stopped.
Due to the function of 6, the lubricating oil cannot be forcibly supplied to the bearings 39, 40.

However, when the differential case 67 is rotated by the power input from the front wheels 71, the ring gear 68
As the lubricating oil D2 is stirred by the rotation of, a part of the lubricating oil D2 is scraped up (pumped up) by the ring gear 68. Then, a part of the lubricating oil D2 scooped up by the ring gear 68 is separated by the centrifugal force into the internal space D2.
It is blown upwards. Here, the axis X1 and the axis Z1 are arranged in parallel, and the input shaft 8
Since the arrangement positions of the bearings 39, 40 and the counter drive gear 36 in the axial direction of the ring gear 68 and the arrangement position of the ring gear 68 are as close as possible, the lubricating oil D2 blown over the internal space D1 is 4 easily reaches the outer peripheral side of the counter drive gear 37 and adheres to the inner wall of the casing 4. Next, the lubricating oil D2 descends along the inner wall of the casing 4 and enters the oil passage 52. Then, the lubricating oil D2 that has entered the oil passage 52 is applied to the bearings 39, 4
0 from the outer peripheral side of the bearing 3
9, 40 are lubricated and cooled. Therefore, even when the vehicle is towed, heat generation, wear and seizure of the bearings 39 and 40 can be suppressed, and the durability thereof is improved.
For this reason, after repairing the faulty part of the vehicle, the bearing 39,
40 can be reused.

A snap ring 51 is provided for restricting the movement of the bearings 39 and 40 in the axial direction.
It is provided facing. The flow of the lubricating oil D2 that has entered the oil passage 52 is smoothly supplied from the opening 53 to the bearings 39 and 40 without being interrupted by the snap ring 51. Therefore, the lubrication and cooling functions for the bearings 39 and 40 are further improved.

Further, since the oil passage 52 is opened between the bearing 39 and the bearing 40, the lubricating oil sent from the oil passage 52 temporarily moves to the inner peripheral side of the bearings 39 and 40 by its own weight. After that, it moves to the outer peripheral side by centrifugal force due to the rotation of the inner rings 41 and 46. Therefore, the lubricating oil is evenly distributed between the inner ring 41 and the outer ring 42 and between the inner ring 46 and the outer ring 47, and the lubricating performance is further improved.

In this embodiment, the lubricating oil D
2 is arranged at the same position in the axial direction as the ring gear 68 that lifts the lubricating oil 2 and the oil passage 52 that supplies the lubricating oil D2 to the bearings 39 and 40. It is easy to enter the oil passage 52. However, since the lubricating oil D2 descends by its own weight along the inner wall of the casing 4, the shape of the inner wall of the casing 4 adheres even if the ring gear 68 and the oil passage 52 are arranged at different positions in the axial direction. If the lubricating oil D2 is shaped to guide the lubricating oil D2 toward the oil passage 52, the lubricating oil D2 can easily enter the oil passage 52 regardless of the positional relationship between the oil passage 52 and the ring gear 68 in the axial direction. Can be maintained.

In the above-described embodiment, the lubricating oil blown off by the ring gear 68 is guided to an oil passage for supplying the differential case 67 or the bearing that rotatably holds the drive shaft 70, and the lubricating oil sent out from this oil passage is guided. Oil may be used to lubricate and cool the bearing.

In this embodiment, the engine is mounted as a driving force source. However, the present invention is also applicable to a vehicle having a motor as a driving force source, or a vehicle having an engine and a motor as a driving force source. This embodiment can be applied. Further, this embodiment can be used for a vehicle equipped with a so-called continuously variable transmission (CVT) that can continuously change the gear ratio as a transmission mechanism.

In the embodiment shown in FIG. 2, the final gear 66 is provided at a position closer to the engine 1 side than the counter driven gear 65, but a position opposite to the engine 1 on the side of the counter driven gear 65. The final gear 66 can also be arranged at the end. Specifically, the bearing 3 in the axial direction of the input shaft 8 is
The final gear 66 can be disposed at the same position as the positions of the positions 9 and 40. In this case, the positions of the bearings 39 and 40 in the axial direction of the input shaft 8 and the position of the ring gear 68 are the same. When this configuration is adopted, there is an effect that the lubricating oil blown off by the ring gear 68 more easily reaches the oil passage 52.

Here, the characteristic configurations of the present invention disclosed based on the above specific examples are listed as follows. That is, the first means is provided inside the casing.
A first rotating member rotatably disposed about an axis, and coupled to the driving force source and the wheels so as to transmit power, and a rotatably disposed about a second axis parallel to the first axis; And a second rotating member coupled to the first rotating member and the wheel so as to be capable of transmitting power, a bearing for rotatably holding the first rotating member, and housed inside the casing. In a lubricating structure of a power transmission device having a lubricating oil and an oil pump driven by the driving force source to supply the lubricating oil to the bearing, the wheel is disposed on an outer peripheral side of the first rotating member in the casing. A lubricating structure for supplying lubricating oil blown by the second rotating member, which is rotated by the power input from the second rotating member, to the bearing side. .

The second means is a rotatable member rotatably disposed inside the casing and connected to the driving force source and the wheels so as to transmit power, and rotatably holds the rotatable member. A bearing, a lubricating oil housed inside the casing, and an oil pump driven by the driving force source to supply the lubricating oil to the bearing side. A lubricating structure for a power transmission device, wherein an oil passage is provided for supplying lubricating oil, which has been rotated and scattered by the power input from the wheels, to the bearing side. In the second means, the casing is provided with a snap ring for restricting the bearing from moving in the axial direction of the first rotating member, and the snap ring has a cut in a part in the circumferential direction. And an opening in the oil passage on the bearing side facing the cut.

The third means is disposed inside the casing so as to be rotatable about the first axis, and is connected to the driving force source and the wheels so as to transmit power.
A rotating member, a second rotating member arranged rotatably about a second axis parallel to the first axis, and connected to the first rotating member and the wheels so as to be capable of transmitting power; A bearing for rotatably holding the first rotating member;
In a lubrication structure for a power transmission device having a lubricating oil contained in the casing, a first rotating member and a second
And a third rotating member (counter shaft) that rotates around a third axis parallel to the first axis and the second axis is provided. A second gear (counter driven gear) meshing with a first gear (counter drive gear) of the first rotating member, and a fourth gear (final gear) meshing with a third gear (ring gear) of the second rotating member. Are provided, the first gear and the bearing are disposed adjacent to each other in the axial direction, and the second gear and the fourth
A gear is disposed adjacently in the axial direction, and lubricating oil blown by the second rotating member rotated by power input from the wheel is provided on the outer peripheral side of the first rotating member in the casing, and the bearing is provided with the bearing. Characterized in that an oil passage to be supplied to the side is provided.

[0059]

As described above, according to the first aspect of the present invention, when the power input from the wheels is transmitted to the second rotating member, the second rotating member rotates to scrape up the lubricating oil. The lubricating oil is blown into the casing by centrifugal force. Here, since the first axis and the second axis are arranged in parallel, the lubricating oil blown into the casing easily reaches the first rotating member side, and this lubricating oil passes through the oil passage. To the bearing side. Therefore, even when the vehicle is towed, the bearing can be lubricated and cooled, and heat generation, wear, and seizure of the bearing can be suppressed.

According to the second aspect of the present invention, in addition to obtaining the same effects as the first aspect of the present invention, the opening of the oil passage on the bearing side is arranged facing the cut of the snap ring. Therefore, when the lubricating oil is sent to the bearing side through the oil passage, the lubricating oil flows smoothly without being hindered by the snap ring, and the lubrication and cooling performance for the bearing is improved.

According to the third aspect of the invention, the same effects as those of the first or second aspect can be obtained, and even when the lubricating oil cannot be blown to the bearing side by the rotation of the first rotating member, the first aspect can be improved. The lubricating oil is blown off by the rotation of the two rotating members, and the lubricating oil is sent to the oil passage. Therefore, the bearing can be reliably lubricated, and the lubrication performance and the cooling performance for the bearing are further improved.

According to the fourth aspect of the present invention, the lubricating oil that has been rotated and scattered by the power input from the wheels is sent to the bearing by the oil passage, and the bearing is lubricated and cooled. Therefore, even when the vehicle is towed, the bearing can be lubricated and cooled, and heat generation, wear, and seizure of the bearing can be suppressed.

[Brief description of the drawings]

FIG. 1 is a partially enlarged sectional view showing one embodiment of a lubrication structure of a power transmission device of the present invention.

FIG. 2 is a skeleton diagram showing a configuration of a transaxle to which the lubrication structure of the power transmission device of the present invention is applied.

FIG. 3 is a view showing a main part of the casing shown in FIG. 2;

FIG. 4 is a schematic sectional view of the casing shown in FIG. 2;

FIG. 5 is a table showing engagement / disengagement of a friction engagement device of the transmission mechanism shown in FIG. 2;

[Explanation of symbols]

1: engine, 4: casing, 35: cylindrical member,
37: counter drive gear, 39, 40: bearing,
51: Snap ring, 51A: Abutment, 52: Oil passage, 53: Opening, 67: Differential case, 68: Ring gear, 71: Wheel, A1, A2, A3: Rotation center, D2: Lubricating oil, X1, Z1 ... Axis.

 ──────────────────────────────────────────────────続 き Continued on the front page F term (reference) 3J063 AA01 AB02 AB12 AC04 BA01 BA05 BA11 BA15 BB34 CA01 CD01 CD41 CD56 XD03 XD17 XD33 XD47 XD62 XD73 XE15 XE37 XH03 XH13 XH42

Claims (4)

[Claims] A first rotating member disposed inside the casing so as to be rotatable about a first axis and connected to a driving force source and wheels so as to be able to transmit power, and parallel to the first axis. A second rotating member rotatably disposed about a second axis and connected to the first rotating member and the wheels so as to be capable of transmitting power, and rotatably holding the first rotating member. In a lubrication structure for a power transmission device having a bearing and lubricating oil housed inside the casing, on the outer peripheral side of the first rotating member in the casing,
A lubrication structure for a power transmission device, further comprising an oil passage for supplying lubricating oil blown by the second rotating member rotated by power input from the wheel to the bearing side. 2. The casing according to claim 1, wherein the bearing is provided with the first bearing.
A snap ring that regulates movement of the rotating member in the axial direction is provided, and a cut is formed in a part of the snap ring in a circumferential direction, and the opening in the oil passage on the bearing side is provided with the snap ring. The lubrication structure for a power transmission device according to claim 1, wherein the lubrication structure is arranged so as to face the cut. 3. The first casing inside the casing.
The height of the lower end of the rotating member is set higher than the height of the lower end of the second rotating member inside the casing, and the level of the lubricating oil is adjusted to the first rotating member. The lubrication structure for a power transmission device according to claim 1, wherein the lubrication structure is set at a position where the power transmission device does not contact and comes into contact with the second rotating member. 4. A rotating member rotatably disposed inside the casing and connected to a driving force source and wheels so as to transmit power, a bearing for rotatably holding the rotating member, and the casing. A lubricating structure of a power transmission device having lubricating oil accommodated in the inside of the power transmission device, wherein lubricating oil, which is rotated by the rotating member by power input from the wheels and is blown to the casing, is supplied to the bearing side. A lubricating structure for a power transmission device, characterized in that a lubricating oil passage is provided.