JP2002327833A - Lubricant feeder for transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a lubricant feeder forming a communication oil passage without thickening a wall surface of a case, easily feeding lubricant to lubricant passages of two opposing rotary shafts, and capable of changing a distribution ratio. SOLUTION: The lubricant feeder for a transmission feeds lubricant to the lubricant passages 74 and 76 respectively formed on the first and second rotary shafts 13 and 15 with opposing end faces rotatably attached inside cases 17 and 18. It has a bulkhead part 18a provided in the case 18 and formed with the communication oil passage 78 opened in one face and communicating with the lubricant passages 74 and 76, and a partition plate 83 attached to the one face of the bulkhead 18a and formed with a distribution hole 84 distributing lubricant flowing into the lubricant passages 74 and 76 from the communication oil passage 78. The partition plate 83 is fixed to the bulkhead 18a by a bearing 52 attached to a one face side of the bulkhead 18a and supporting the rotary shaft 15.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a lubricating oil supply device for a transmission.

[0002]

2. Description of the Related Art Lubricating oil supplied to a bearing or the like provided on a rotating shaft of a transmission is cooled by an oil cooler provided separately from the transmission, and is rotated from outside of a case of the transmission via a communication oil passage. The oil is supplied to a lubricating oil passage formed inside the shaft, and is distributed radially from the shaft center by centrifugal force.

In such a lubricating oil supply device for a transmission, a communication oil passage for guiding the lubricating oil from the outside of the case to the lubricating oil passage has been formed inside a thick wall surface of the case.

[0004]

However, in such a structure of the communication oil passage, the wall surface of the case needs to be formed thick for the oil passage. Further, when distributing the lubricating oil from the communication oil passage to two rotating shafts facing each other with the wall surface of the case as a boundary, a distribution oil passage is further formed in the case.
It has been difficult to reduce the size and weight of the transmission.

[0005] A first object of the present invention is to provide a lubricating oil supply device which can form a communication oil passage without increasing the thickness of the wall of a case and can reduce the size of a transmission.

A second object of the present invention is to provide a lubricating oil supply device capable of supplying lubricating oil to two opposed rotating shafts without increasing the size of the transmission.

[0007]

To achieve the first object, a lubricating oil supply device for a transmission according to the present invention has a rotating shaft rotatably mounted in a case, and is formed on the rotating shaft. A lubricating oil supply device for a transmission that supplies lubricating oil to the lubricating oil passage, wherein the partition is formed in the case, and a communication oil passage communicating with the lubricating oil passage is formed by opening on one surface. ,
A partition plate attached to one surface of the partition wall and closing the opening.

In order to achieve the second object, a lubricating oil supply device for a transmission according to the present invention has first and second rotating shafts rotatably mounted in a case with their end faces facing each other,
A lubricating oil supply device for a transmission for supplying lubricating oil to a lubricating oil passage formed on each of the rotating shafts, wherein a communication oil passage provided in the case and communicating with each of the lubricating oil passages has one surface. And a distribution hole attached to one surface of the partition portion for closing the opening and distributing the amount of lubricating oil flowing from the communication oil passage to each of the lubricating oil passages. And a partition plate on which is formed.

In the lubricating oil supply device for a transmission according to the present invention, the partition plate is fixed to the partition wall by a bearing mounted on one surface of the partition wall and supporting one of the rotating shafts. .

[0010] By attaching a partition plate to the opening of the partition formed by opening the communication oil passage on one side, a communication oil passage can be formed by the opening and the partition plate. Therefore, the wall thickness of the partition can be reduced, and the transmission can be reduced in size and weight.

By forming a distribution hole in the partition plate, the lubricating oil can be easily guided to another system. Further, the supply amount can be easily changed by changing the diameter of the distribution hole.

By fixing the partition plate to the case using a bearing that supports the rotating shaft, the partition plate can be fixed without increasing the number of parts, and oil leakage from the partition plate can be prevented.

[0013]

Embodiments of the present invention will be described below in detail with reference to the drawings.

FIG. 1 is a skeleton diagram showing a power transmission device 9 according to an embodiment of the present invention. As shown in FIG. 1, a power transmission device 9 having the transmission 10 is connected to an engine 11 and is connected to an engine 11 via a torque converter 12. It has a front wheel output shaft 14 to be connected, and a rear wheel output shaft 15 parallel to the input shaft 13 and connected to the rear wheel. Input shaft 13, front wheel output shaft 14, rear wheel output shaft 15
Is installed in the transmission case 16 in the traveling direction of the vehicle, and the transmission 10 can be applied to a four-wheel drive vehicle arranged vertically. The transmission case 1
The rear case output shaft 15 is housed in a transfer case 17 forming one end of the motor case 6, and the one end of the input shaft 13 is housed in a bypass case 18 adjacent to the transfer case 17.

A torque converter 12 is connected to the engine 11, and an oil pump 20 is connected to the torque converter 12.
Is connected, the oil pump 20
Driven by

The input shaft 13 is integrally provided with first and second speed drive gears 21a and 22a, and third to sixth speed drive gears 23a to 26a are rotatably provided. The front wheel output shaft 14 has first and second speed driven gears 21b, 22
b is provided rotatably, and the driven gear 2 of the third to sixth speeds
3b to 26b are provided integrally. Drive gears 21a-2
The gear 6a and the driven gears 21b to 26b are meshed with each other to form a transmission gear train for forward movement.

On the front wheel output shaft 14, a first switching mechanism 31 for switching the speed change gear train between the first speed and the second speed is mounted, and on the input shaft 13, the speed change gear train is connected to the fourth speed and the fifth speed. And a third switching mechanism 33 for switching the speed change gear train to the sixth speed. Each of the switching mechanisms 31 to 33 includes a synchro sleeve 31b to 33b provided on the synchro hub 31a to 33a so as to be slidable in the axial direction, and gears 21b and 22.
b, splines 21 provided integrally with 24a to 26a
It is a synchromesh mechanism that engages in synchronization with c, 22c, 24c to 26c.

At one end of the input shaft 13 in the bypass case 18, a bypass clutch 41 is provided. The bypass clutch 41 includes a clutch hub 41 a fixed to the input shaft 13 and a third clutch rotatably mounted on the input shaft 13.
Drum 41b fixed to high-speed drive gear 23a
And By pressing a plurality of bypass clutch plates 44 provided alternately on the clutch hub 41a and the clutch drum 41b, the bypass clutch 41 is brought into the engaged state in which the input shaft 13 and the third speed drive gear 23a are engaged. Can be linked.

A drive gear 45a for retreat is integrally provided on the input shaft 13, and a driven gear 45b for retreat is provided on the front wheel output shaft 14 with the synchro hub 31a and the synchro sleeve 31b.
And are connected through. An idler gear 45c is rotatably mounted on the idler shaft 46 disposed parallel to the input shaft 13, and when the idler gear 45c moves along the idler shaft 46, the idler gear 45c meshes with the drive gear 45a and the driven gear 45b. Engage. Thus, the driving gear 4
The gear 5a, the driven gear 45b, and the idler gear 45c form a reverse gear train. Further, the idler gear 45
The fourth switching mechanism 34 for switching the transmission gear train to the reverse is provided at c.
Is mounted, and the reverse speed change gear train is provided with a fourth switching mechanism 34.
Is selectively slidable in which switching is performed by actuating a switching member 34a provided in the system.

A drive pinion 46 is provided at one end of the front wheel output shaft 14. A drive shaft (not shown) for front wheels is provided via a front differential device 47.
It is connected to. The other end of the front wheel output shaft 14 has a transfer drive gear 4 for transmitting a driving force to the rear wheel output shaft 15.
8a are provided.

At the end of the rear wheel output shaft 15 housed in the transfer case 17, a transfer driven gear 48b meshing with a transfer drive gear 48a is rotatably mounted. Further, a friction clutch 49 is mounted on the rear wheel output shaft 15. The friction clutch 49 includes a clutch hub 49 a fixed to the rear wheel output shaft 15 and a rear wheel output shaft 1.
5 is rotatably mounted on the transfer driven gear 48b
And a clutch drum 49b fixed to the front wheel output shaft 14 by engaging the friction clutch 49.
Is transmitted to the rear wheel output shaft 15. Rear wheel output shaft 1
Reference numeral 5 is connected to a rear wheel drive shaft (not shown) via a rear differential device (not shown).

The shifting operation of the transmission 10 will be described. The switching of the first speed is performed by engaging the synchro sleeve 31b of the first switching mechanism 31 with the spline 21c. At this time, the driving force of the input shaft 13 is changed from the input shaft 13 to the driving gear 21a, the driven gear 21b,
The power is transmitted to the front wheel output shaft 14 via the first switching mechanism 31. Synchro sleeve 31b with spline 22
When engaged with c, the transmission gear train can be switched to the second speed. Similarly, switching between the fourth speed and the fifth speed is performed by operating the second switching mechanism 32, and switching of the sixth speed is performed by operating the third switching mechanism 33.

The switching of the third speed is performed by the bypass clutch 41.
The driving force is transmitted from the input shaft 13 to the bypass clutch 41, the driving gear 23a, and the driven gear 2
The power is transmitted to the front wheel output shaft 14 via 3b.

The reversing is switched by operating a switching member 34a provided in the fourth switching mechanism 34 so that the driving gear 45a for retreating and the driven gear 45b are connected to the idler gear 4a.
5c, and the driving force of the input shaft 13 is transmitted to the front wheel output shaft 14 with the rotation direction reversed.

The first to third switching mechanisms 31 to 33 include splines 21c, 22c, 24c to 26c installed on both sides.
The fourth switching mechanism 34 can control the drive gear 45a and the driven gear 45b to a neutral state in which the idler gear 45c does not mesh with the synchronous gears 31b to 33b. The plurality of switching mechanisms 31 to 34 do not mesh at the same time during traveling, and when switching to the third speed, all switching mechanisms 31 to 34 are used.
34 is controlled to a neutral state. Further, when the transmission gear train is switched, the driving torque is interrupted by the neutral state of the switching mechanisms 31 to 33, and a feeling of pull-in occurs. In order to eliminate the feeling of pull-in, the bypass clutch 41 is controlled so that the drive torque of the input shaft 13 is appropriately transmitted to the front wheel output shaft 14 via the bypass clutch 41.

When the friction clutch 49 mounted on the rear wheel output shaft 15 is disengaged, the distribution ratio of the driving torque transmitted to the front wheels and the rear wheels becomes 100: 0, and the rear wheels are not driven and the front wheels are driven. You can run as a car. on the other hand,
When the friction clutch 49 is controlled to be in the direct connection state in which the friction clutch 49 is completely engaged, the drive torque distribution ratio to the front and rear wheels is 50:50,
It can run as a four-wheel drive vehicle. By controlling the engagement of the friction clutch 49 between the disengaged state and the directly connected state, the drive torque distribution ratio to the front and rear wheels can be controlled between 100: 0 and 50:50. For example, when driving suddenly or when traveling on a slippery road surface, the driving torque can be transmitted to both the front and rear wheels for stable driving, and during steady driving, only the front wheels transmit driving torque to reduce fuel consumption. Can be reduced.

The running condition is determined based on the vehicle speed, the throttle opening, the difference between the front and rear wheels, the braking operation, and the like, and the operation of the friction clutch 49 is controlled in accordance with the running condition. For this reason, the operation of the friction clutch 49 requires slip control to slide the clutch plate 50, that is, clutch capacity control. In the friction clutch 49 in which the clutch piston 51 operates by hydraulic pressure, the pressure receiving area of the clutch piston 51 is reduced. By enlarging, even if the hydraulic control valve is the same, it becomes possible to perform clutch displacement control with high accuracy.

FIG. 2 is a sectional view showing a part of the power transmission device 9 in FIG. As shown in FIG. 2, a transfer drive gear 48a fixed to the front wheel output shaft 14 is disposed in the transfer case 17. A rear wheel output shaft 15 that is a rotating shaft is mounted on the transfer case 17 and is rotatably supported by a first bearing 52 and a second bearing 53. A transfer driven gear 48b is rotatably mounted on the rear wheel output shaft 15, and meshes with the transfer drive gear 48a.

A friction clutch 49 is provided on the rear wheel output shaft 15 adjacent to the transfer driven gear 48b. Hereinafter, the structure of the friction clutch 49 will be described.

Adjacent to the transfer driven gear 48b,
A clutch hub 49a is fixed to the rear wheel output shaft 15. A clutch drum 49b is disposed radially outward of the clutch hub 49a, and the clutch drum 49b is fixed to a transfer driven gear 48b. Clutch hub 4
A plurality of drive plates 50a are slidably mounted in the axial direction on the outer side in the radial direction of the clutch drum 49a.
A plurality of driven plates 50b are mounted slidably in the axial direction on the inner side in the radial direction. Clutch plate 5
The drive plates 50a and the driven plates 50b which are 0 are alternately arranged. A fastening member 54 is mounted inside the end of the clutch drum 49b so as to be slidable in the axial direction, and the drive plate 50a and the driven plate 50b are fastened to each other by sliding the fastening member 54 in the axial direction. You.

A clutch cylinder 56 provided separately from the transfer case 17 is attached to the transfer case 17 in which the friction clutch control oil passage 55 is formed.
It is fixed to the transfer case 17 by a screw member 57. Clutch cylinder 56 is transfer case 1
Outer cylindrical portion 56a formed radially outward until it contacts with No. 7
And an inner cylindrical portion 56b formed radially inward near the rear wheel output shaft 15, an outer cylindrical portion 56a, and an inner cylindrical portion 56b.
And an end wall portion 56c formed between the transfer case 17 and the transfer case 17. The clutch piston 56 is slidably accommodated in the clutch cylinder 56, and a hydraulic chamber 58 is formed by the clutch cylinder 56 and the clutch piston 51. Further, the end wall portion 56
c has a communication hole 60 communicating with the friction clutch control oil passage 55.
Is formed, and the hydraulic oil guided to the friction clutch control oil passage 55 can be supplied to the hydraulic chamber 58.

A bearing support 61 is formed radially inward of the clutch piston 51, the inner ring of the third bearing 62 is fitted to the bearing support 61, and the outer ring of the third bearing 62 is fitted to the fastening member 54. Mated. That is, the clutch piston 51
And the fastening member 54 are connected via a third bearing 62. A spring member 63 is mounted between the clutch cylinder 56 and the clutch piston 51 so as to release the friction clutch 49 from engagement. Further, a rotation stopping portion 64 protruding radially outward of the clutch piston 51 is formed, and a cutout 65 corresponding to the rotation stopping portion 64 is formed radially outward of the clutch cylinder 56. The contact between the rotation stopping portion 64 and the notch portion 65 restricts the rotation of the clutch piston 51 and limits the movement to sliding only in the axial direction.

By supplying hydraulic oil to the hydraulic chamber 58 by such a friction clutch 49, the clutch piston 5
1 slides the fastening member 54 via the third bearing 62. The slide of the fastening member 54 causes the drive plate 50a
And the driven plate 50b are fastened, and the driving force of the clutch drum 49b is transmitted to the clutch hub 49a. As a result, the driving force of the transfer driven gear 48b is transmitted to the rear wheel output shaft 15.

The clutch cylinder 56 is fixed to the transfer case 17, and the rotation of the clutch piston 51 is stopped.
The hydraulic oil in 8 can control the clutch piston 51 without being affected by the centrifugal force.

By transmitting the operation of the clutch piston 51 to the fastening member 54 via the large-diameter third bearing 62, the contact surface between the fastening member 54 and the third bearing 62, the fastening member 54 and the clutch plate The distance in the radial direction with respect to the contact surface with 50 can be reduced, and the bending rigidity of the fastening member 54 can be increased. Therefore, the bending deformation due to the bending moment applied to the fastening member 54 is reduced, and the surface pressure applied to the clutch plate 50 can be made uniform.

Further, by providing the rotation stopping portion 64 radially outward of the clutch piston 51, the inner cylinder portion 56b of the clutch cylinder 56 can be provided close to the rear wheel output shaft 15, and the clutch piston 51 The pressure receiving area can be maximized in the transfer case 17. By providing the clutch cylinder 56 separately from the transfer case 17, it is possible to manufacture the clutch cylinder 56 using a material having high rigidity to reduce the thickness of the inner cylindrical portion, and further secure the pressure receiving area of the clutch piston 51. can do. As a result, highly accurate clutch capacity control becomes possible.

Further, both sides of the transfer driven gear 48b and the friction clutch 49 are connected to the first bearing 52 and the second bearing 5 respectively.
3, the bending caused by the bending moment applied to the clutch drum 49b when the friction clutch 49 is engaged and disengaged,
Vibration noise at the transfer gears 48a and 48b can be suppressed without being transmitted to the transfer driven gear 48b fixed to the transfer gear 9b.

Hereinafter, the supply of the lubricating oil will be described. As shown in FIG. 1, the hydraulic oil discharged from the oil pump 20 is supplied to a lubrication unit after being guided by a cooling passage 70 and cooled through an oil cooler 71 to be used as a lubricating oil.

One end of an input shaft 13 is mounted on a bypass case 18 adjacent to the transfer case 17, and a third speed drive gear 23a is rotatably provided on the input shaft 13, and the input shaft 13 and the third A bypass clutch 41 for engaging or disengaging the high-speed drive gear 23a is mounted. Also, as shown in FIG. 2, the third speed drive gear 23a
Needle bearing 7 mounted between the shaft and the input shaft 13
2. A lubricating oil path for supplying lubricating oil to a lubricating portion including a bypass clutch plate 44 mounted on the bypass clutch 41 and a needle bearing 73 mounted between the input shaft 13 and the bypass case 18, that is, a bypass. A lubricating oil passage 74 is formed inside the input shaft 13 that is the first rotating shaft.

Similarly, the transfer case 17 includes a needle bearing 75 disposed between the transfer driven gear 48b and the rear wheel output shaft 15, a clutch plate 50 mounted on the friction clutch 49, and a rear wheel output. A lubricating oil passage for supplying lubricating oil to a lubricating portion comprising a second bearing 53 supporting the shaft 15, that is, a transfer lubricating oil passage 76
Are formed inside a rear wheel output shaft 15 which is a second rotation shaft.

A cooling path connecting portion 77 for connecting the cooling path 70 is formed inside the partition 18a facing the transfer case 17 of the bypass case 18, and communicates with the cooling path connecting 77 inside the partition 18a. Thus, a communication oil passage 78 is formed. Further, an opening 79 is formed in the partition wall portion 18a so that a communication oil passage 78 is opened on one side, and a communication hole 80 penetrating the partition wall is formed in the center of the opening portion 79. Further, a bearing support surface 81 is formed in the partition wall portion 18a around the communication hole 80, and a partition plate contact surface 82 is formed orthogonal to the bearing support surface 81.

FIG. 3 shows the bypass case 18, the partition plate 83,
FIG. 2 is an exploded perspective view showing a positional relationship between the first bearing 52 and the first bearing 52. As shown in FIG. 2 and FIG. 3, a circular and thin partition plate 83 is formed on the partition plate contact surface 8 formed on the partition wall portion 18a.
It is attached in contact with 2. A distribution hole 84 communicating with the communication hole 80 of the bypass case 18 is formed at a central portion of the partition plate 83, and an outer peripheral portion of the partition plate 83 is formed thicker than the central portion.

Bearing support surface 81 formed on partition wall portion 18a
Supports the outer ring of the first bearing 52. The outer ring and the outer peripheral portion of the partition plate 83 come into close contact with each other, and the partition plate 83
And is fixed in close contact with the partition plate contact surface 82 by the bearing 52. The rear wheel output shaft 15 is formed by the inner ring of the first bearing 52.
Are rotatably supported.

By connecting the cooling passage 70 to the cooling passage connecting portion 77 using the connecting member 85 in the bypass case 18, the cooled lubricating oil guided to the cooling passage 70 allows the connecting member 85 to be connected. The lubricating oil is supplied to the communication oil passage 78 through the communication passage 78 formed by the opening 79 and the partition plate 83, and supplied from the communication oil passage 78 to the communication hole 80. Lubricating oil is supplied to each of the bypass lubricating oil passage 74 and the transfer lubricating oil passage 76 provided facing the bypass case 18 and the partition plate 83 from the communication holes 80.

The bypass lubricating oil passage 74 is supplied with lubricating oil directly from the communication hole 80, and the transfer lubricating oil passage 76 is provided with a distribution hole 84 formed in the partition plate 83 through the communication hole 80.
The lubricating oil is supplied through. In the case shown in FIG. 2, the bypass clutch 41 that is engaged at the time of gear shifting and reduces a drop in transmission torque is less than the friction clutch 49 that is engaged when transmitting driving force to the rear wheels due to slippage of the front wheels. Are frequently fastened, resulting in a large amount of heat generation. Therefore, it is necessary to supply a large amount of lubricating oil to the bypass clutch 41, and the distribution holes 8 formed in the partition plate 83 are formed.
4, the ratio of the lubricating oil supplied from the communication hole 80 to the bypass lubricating oil passage 74 and the transfer lubricating oil passage 76 is changed. When the distribution hole 84 is enlarged, the ratio of the lubricating oil supplied to the transfer lubricating oil passage 76 increases, and when the distribution hole 84 is reduced, the ratio decreases.

With such a lubricating oil supply device, the thickness of the partition wall portion 18a can be formed without increasing the thickness for the communication oil passage 78, and the transmission can be downsized. In addition, since a part of the communication oil passage 78 can be processed as the opening 79, the processing can be easily performed. Further, since the flow path 86 is formed by using the partition plate 83, when the partition plate 83 having no distribution hole 84 is mounted, lubricating oil can be supplied only in one direction, and the distribution hole 84 is provided. When the partition plate 83 is attached, lubricating oil can be supplied in two directions. Depending on the size of the distribution hole 84 to be formed, the ratio of the lubricating oil supplied in two directions can be easily changed without processing the bypass case 18.

The present invention is not limited to the above-described embodiment, and it goes without saying that various modifications can be made without departing from the scope of the present invention. For example, the illustrated partition plate 83 is circular, but is not limited to a circular shape.
The illustrated transmission is a torque converter type automatic transmission and is for a vertical four-wheel drive vehicle, but this lubricating oil supply device can also be used for a continuously variable transmission or a manual transmission,
It can be used for horizontal installation and even for two-wheel drive vehicles. Although an opening is provided in the partition of the bypass case 18, the partition may be formed in the transfer case 17 to provide the opening.

[0048]

As described above, according to the present invention, the partition plate is attached to the opening of the partition formed by opening the communication oil passage on one side, so that the opening and the partition plate can be used. A communication oil passage can be formed. Therefore, the wall thickness of the partition can be reduced, and the transmission can be reduced in size and weight.

By forming the distribution holes in the partition plate, the lubricating oil can be easily guided to another system. Further, the supply amount can be easily changed by changing the diameter of the distribution hole.

By fixing the partition plate to the case using a bearing that supports the rotating shaft, the partition plate can be fixed without increasing the number of components, and oil leakage from the partition plate can be prevented.

[Brief description of the drawings]

FIG. 1 is a skeleton diagram showing a transmission having a lubricating oil supply device according to an embodiment of the present invention.

FIG. 2 is a sectional view of the lubricating oil supply device in FIG.

FIG. 3 is an exploded perspective view showing a positional relationship among a bypass case, a partition plate, and a bearing.

[Explanation of symbols]

 Reference Signs List 13 input shaft (first rotating shaft) 15 rear wheel output shaft (second rotating shaft) 17 transfer case (case) 18 bypass case (case) 18a partition wall portion 52 first bearing (bearing) 74 bypass lubricating oil passage (Lubricating oil passage) 76 Transfer lubricating oil passage (lubricating oil passage) 78 Communication oil passage 79 Opening 83 Partition plate 84 Distribution hole

Claims (3)

[Claims] 1. A lubricating oil supply device for a transmission, having a rotating shaft rotatably mounted in a case, for supplying lubricating oil to a lubricating oil passage formed in the rotating shaft. It is provided, characterized in that it has a partition portion formed by opening a communication oil passage communicating with the lubricating oil passage on one side, and a partition plate attached to one surface of the partition portion and closing the opening. A lubricating oil supply device for a transmission. 2. A case having first and second rotating shafts rotatably mounted in a case with their end faces facing each other, and supplying lubricating oil to a lubricating oil passage formed in each of the rotating shafts. A lubricating oil supply device for a transmission, comprising: a partition provided in the case, and formed with a communication oil passage communicating with each of the lubrication oil passages opened on one surface; A lubricating gear for a transmission, wherein the lubricating oil passage is provided with a partition plate which closes an opening and has a distribution hole formed therein for distributing an amount of lubricating oil flowing into the lubricating oil passage from the communication oil passage. Oil supply device. 3. The lubricating oil supply device for a transmission according to claim 2, wherein the partition plate is fixed to the partition wall portion by a bearing mounted on one surface side of the partition wall portion and supporting one of the rotating shafts. A lubricating oil supply device for a transmission.