JPH06109105A - Lubrication structure for planetary gear mechanism - Google Patents

Abstract

PURPOSE:To prevent seizure of a pinion gear supporting bearing by supplying lubricating oil to the pinion gear supporting bearing with certainty from a direction substantially the same as the arrangement direction of a lubricating oil passage. CONSTITUTION:An intermediate gear 5 is rotatably supported to a transmission case 3 through tapered roller bearings 41, 42. A pinion shaft 51 of a front planetary gear mechanism 21 is arranged near the side of an axially large diameter portion of the tapered roller bearing 41. A lubricating oil passage 54 is formed on the pinion shaft 51. The oil passage 54 is opened to the side of the large diameter part of the tapered roller bearing 41 at its one end, extended in an axial direction of the pinion shaft 51, radially extended from a portion near an axial center of a bearing 53 for supporting a pinion gear, opened at the pinion gear supporting bearing 53 at the other end, for introducing lubricating oil from the large diameter side of the tapered roller bearing 41 to the bearing 53.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a lubrication structure for a planetary gear mechanism, and more particularly to a lubrication measure for a bearing that supports a pinion gear on a pinion shaft.

[0002]

2. Description of the Related Art Generally, in a power transmission mechanism such as a transmission, a power transmission member rotatably supported in a case of the power transmission mechanism is disclosed in Japanese Patent Laid-Open No. 1-238736. The driving force (rotational force) from the shaft
The output of the planetary gear mechanism arranged on the shaft is appropriately changed by changing the transmission path, and the shaft of the power transmission member is supported to the case of the power transmission mechanism via a tapered roller bearing. It is supposed to be done. Lubrication of the planetary gear mechanism and the tapered roller bearing is performed by the oil sprinkled by centrifugal force through a hole opening in the oil passage in the shaft of the power transmission member.

Further, as a lubrication measure for a portion which is difficult to be supplied with the oil sprinkled by the centrifugal force as described above, particularly a bearing for rotatably supporting the pinion gear on the pinion shaft of the planetary gear mechanism, one end of the pinion shaft is used. One side of the pinion shaft is opened and the other end is opened in the vicinity of the bearing to provide a lubricating oil passage for guiding lubricating oil from one side of the pinion shaft to the bearing. There is also an oil path that receives and collects the oil (lubrication oil) sprinkled by the oil so that the bearings for supporting the pinion gear can be lubricated with sufficient lubricating oil in the oil path (actually developed. 58-67161
(See Japanese Patent Publication).

[0004]

However, in the case where the above-mentioned bearing for supporting the pinion gear is lubricated, the direction of the lubricating oil passage extending from one side surface of the pinion shaft to the bearing and the power transmission member. Since the direction in which the lubricating oil is sprinkled by the centrifugal force of the shaft is orthogonal, the lubricating oil that has accumulated in the oil path cannot be positively guided into the lubricating oil passage, and the bearings for supporting the pinion gear may seize. was there.

The present invention has been made in view of the above points, and an object thereof is to reliably supply the lubricating oil to the bearing for supporting the pinion gear from a direction substantially coincident with the arrangement direction of the lubricating oil passage. Thus, the seizure of the bearing for supporting the pinion gear is prevented.

[0006]

In order to achieve the above-mentioned object, the means for solving the problems according to the invention described in claim 1 is as a lubrication structure of a planetary gear mechanism, in which a power transmission member of a power transmission mechanism is provided via a tapered roller bearing. And a pinion shaft of the planetary gear mechanism is arranged adjacent to the tapered roller bearing on the side of the large diameter portion in the axial direction. Then, one end of the above-mentioned pinion shaft is opened to the large diameter side of the tapered roller bearing, and the other end is opened near the bearing that supports the pinion gear on the pinion shaft to lubricate from the large diameter side of the tapered roller bearing to the bearing. The configuration is such that a lubricating oil passage for guiding oil is provided.

Further, the solution means taken by the invention of claim 2 limits the power transmission member of the invention of claim 1 to be an output gear of a transmission. The pinion shaft is supported by the output gear.

[0008]

With the above construction, in the invention according to claim 1,
The lubricating oil sprinkled by the centrifugal force of the shaft of the power transmission member is guided from the small diameter portion side to the large diameter portion side while lubricating the tapered roller bearing itself by the pumping action by the centrifugal force of the tapered roller bearing. In that case, since the pinion shaft of the planetary gear mechanism is arranged close to the side of the tapered roller bearing in the axial direction of the large diameter portion,
The direction in which the lubricating oil is supplied by the centrifugal action of the tapered roller bearing and the direction in which the lubricating oil passage of the pinion shaft, which has one end open to the large diameter side of the tapered roller bearing, are aligned are approximately the same. Lubricating oil positively supplied from the large diameter side can be reliably guided to the bearing for supporting the pinion gear via the lubricating oil passage of the pinion shaft.

According to the second aspect of the invention, since the pinion shaft is supported by the output gear of the transmission,
The support rigidity of the pinion shaft is increased by the output gear.

[0010]

As described above, according to the lubrication structure of the planetary gear mechanism in the invention described in claim 1, the pinion shaft of the planetary gear mechanism is arranged close to the lateral side of the tapered roller bearing in the axial direction of the large diameter portion. Due to this, the supply direction of the lubricating oil due to the centrifugal action of the tapered roller bearing and the installation direction of the lubricating oil passage of the pinion shaft that opens to the large diameter portion side of the tapered roller bearing are substantially the same, and the large diameter portion of the tapered roller bearing is It is possible to reliably guide the lubricating oil positively supplied from the side to the bearing for supporting the pinion gear, and prevent seizure of the bearing for supporting the pinion gear.

According to the lubrication structure of the planetary gear mechanism of the present invention, the pinion shaft is supported by the output gear of the transmission, so that the support rigidity strength of the pinion shaft is increased by the output gear and the planetary gear mechanism is improved. The support rigidity strength of the gear mechanism can be improved.

[0012]

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

FIG. 2 shows an automatic transmission to which a lubrication structure of a planetary gear mechanism according to an embodiment of the present invention is applied. The automatic transmission 1 has a torque converter 10 and the same axis as the torque converter 10. The main transmission 20 is arranged, and the sub transmission 30 is arranged on an axis parallel to these axes.

The torque converter 10 includes a pump 12 integrated with a case 11 connected to the engine output shaft 2,
A turbine 13 arranged to face the pump 12 and driven by the pump 12 via hydraulic oil, and disposed between the pump 12 and the turbine 13 and supported by the transmission case 3 via a one-way clutch 14. Stator 1
5, the converter output shaft 16 connected to the turbine 13, and the converter output shaft 1 via the case 11.
6 and a lockup clutch 17 that directly connects the engine output shaft 2.

The torque converter 10 and the main transmission 2
An oil pump 4 driven by the engine output shaft 2 via the torque converter 10 is disposed between the oil pump 4 and the engine.

The main transmission 20 has a converter output shaft 1
6 has a front planetary gear mechanism 21 arranged on the torque converter side and a rear planetary gear mechanism 22 arranged on the counter torque converter side. The converter output shaft 16 is connected to the sun gear 21a of the front planetary gear mechanism 21 via the forward clutch 23 and the sun gear 2 of the rear planetary gear mechanism 22 via the direct coupling clutch 24.
The sun gear 21a of the front planetary gear mechanism 21 and the ring gear 22b of the rear planetary gear mechanism 22 are coupled to each other.

Further, a first one-way clutch 25 and a low reverse brake 26 are arranged in parallel between the ring gear 21b of the front planetary gear mechanism 21 and the transmission case 3, and the rear planetary gear mechanism 22 has a structure. A second one-way clutch 27 and a 3-4 brake 28 are arranged in series between the sun gear 22a and the transmission case 3, and a coast brake 29 for engine braking is arranged in parallel with them. Then, the pinion carriers 21c, 22c of the front planetary gear mechanism 21 and the rear planetary gear mechanism 22 are coupled, and these are connected to the main transmission 2
An intermediate gear 5 is connected as an output gear that transmits power from 0 to the auxiliary transmission 30.

With such a configuration, the main transmission 20
According to the above, the forward clutch 23, the direct coupling clutch 24,
By selectively engaging the 3-4 brake 28 and the low reverse brake 26, a forward low speed stage, a medium high speed stage, a high speed stage and a reverse stage can be obtained.

On the other hand, the sub-transmission 30 has a single planetary gear mechanism 31, and the intermediate gear 6 which is always meshed with the intermediate gear 5 in the main transmission 20 is connected to the ring gear 31a of the planetary gear mechanism 31. And the ring gear 31
A direct coupling clutch 32 is arranged between a and the sun gear 31b, and a third one-way clutch 33 and a reduction brake 34 are arranged in parallel between the sun gear 31b and the transmission case 3. Then, the planetary gear mechanism 31
The output gear 7 is connected to the pinion carrier 31c of the left and right drive wheels (not shown) from the gear 7 through a differential device.
Power is transmitted to.

The sub-transmission 30 can shift the power input from the main transmission 20 via the intermediate gears 5 and 6 to two forward gears, a low-speed gear and a high-speed gear, and output it to the output gear 7. It is like this.

That is, when the direct coupling clutch 32 is released, the sun gear 31 of the planetary gear mechanism 31 is driven by the third one-way clutch 33 or the reduction brake 34.
By fixing b, the power from the intermediate gear 6 input to the ring gear 31a of the planetary gear mechanism 31 is decelerated and output from the pinion carrier 31c to the output gear 7, whereby a low speed stage is obtained. In this case, if the deceleration brake 34 is engaged, the auxiliary transmission 30
As a single unit, the engine brake will operate.

Further, the direct coupling clutch 32 is engaged,
If the deceleration brake 34 is released, the ring gear 31a and the sun gear 31b of the planetary gear mechanism 31 are coupled to each other, whereby the power from the intermediate gear 6 is directly output from the pinion carrier 31c to the output gear 7.
As a result, a high speed stage (direct connection stage) can be obtained.

In this way, the main transmission 20 can obtain three forward and one reverse gears, and the auxiliary transmission 3
By setting 0, two high and low shift speeds can be obtained with respect to the output of the main transmission 20, so the overall automatic transmission can obtain 6 shift speeds for forward movement and main shifts for reverse movement. The combination of the reverse gear of the machine 20 and the low gear of the auxiliary transmission 30 to which the deceleration brake 34 is engaged provides the reverse gear as a whole. And in this example,
As the forward shift speed, a predetermined five speeds (for the first speed to the fifth speed) out of the above six speeds are adopted.

Here, the operating states of the clutches and brakes at each of the five forward speeds and one reverse speed are summarized in Table 1. In addition, in Table 1, a black circle indicates that only the range for engine braking is engaged.

[0025]

[Table 1] In this embodiment, taper roller bearings 41 and 42 as shown in FIG. 1 are adopted as bearings that rotatably support the intermediate gear 5 with respect to the transmission case 3.

That is, the tapered roller bearing 41,
42 are arranged so that the small-diameter portion sides thereof face each other in the axial direction of the converter output shaft 16, and the axis lines of the taper roller bearings 41 and 42 are arranged to approach the converter output shaft 16 side on the side of the small-diameter portion sides of each other. Is inclined to. The inner races 41a and 42a of the tapered roller bearings 41 and 42 are the same as the converter output shaft 16 described above.
The outer races 41b, 42b are connected to the transmission case 3 while the outer races 41b and 42b are connected to the corresponding free-fitting portion 5a of the intermediate gear 5 in a loosely fitted state. The movement in the direction is regulated.

Further, the converter output shaft 16 is provided with an oil passage 43 connected to a discharge port of an oil pump (not shown), and the converter output shaft 16 is radially arranged at a predetermined position in the axial direction of the converter output shaft 16. There is provided a communication hole 44 that penetrates through and communicates with the oil passage 43. Further, a through hole 45 penetrating in the radial direction of the converter output shaft 16 is provided in the loose fitting portion 5a of the intermediate gear 5 corresponding to between the tapered roller bearings 41 and 42.
Furthermore, the sun gear 21 of the front planetary gear mechanism 21 is
The coupling member 46 that couples a with the ring gear 22b of the rear planetary gear mechanism 22 has an outer fitting portion 46a that is fitted with the converter output shaft 16 so as to be rotatable relative to the converter output shaft 16. A through hole 47 penetrating in the radial direction of the converter output shaft 16 is also provided between the portions 42, that is, in the outer fitting portion 46a corresponding to the through hole 45a.

And, on the side of the large diameter portion in the axial direction of the tapered roller bearing 41 on the front planetary gear mechanism side,
The pinion shaft 51 of the front planetary gear mechanism 21 is arranged closely. The pinion shaft 51 has a tapered roller bearing side portion which is a loose fitting portion 5 of the intermediate gear 5.
It is fixed directly outside. A pinion gear 52 that meshes with the sun gear 21 a and the ring gear 21 b is supported on the pinion shaft 51 via a bearing 53. Then, one end of the pinion shaft 51 opens toward the large diameter portion side of the taper roller bearing 41 and extends in the axial direction of the pinion shaft 51, and then the diameter of the bearing 53 for supporting the pinion gear from the vicinity of the central portion in the axial direction. A lubricating oil passage 54 is provided that extends radially in the direction and has the other end opened to the bearing 53 for supporting the pinion gear and guiding the lubricating oil from the large diameter portion side of the tapered roller bearing 41 to the bearing 53. .
Although not shown, a similar lubricating oil passage is also provided in the pinion shaft of the rear planetary gear mechanism 22.

Therefore, in the above embodiment, the centrifugal force of the converter output shaft 16 causes the oil passage 43 to communicate with the communication hole 4.
The lubricating oil sprinkled from the through hole 47 of the outer fitting portion 46a of the coupling member 46 via the Nos. 4 and 44 passes through the through hole 45 of the loose fitting portion 5a of the intermediate gear 5 and the tapered roller bearing 4
After being introduced between the first and second tapered roller bearings 41 and 42, the tapered roller bearings 41 and 42 are guided by the centrifugal force of the tapered roller bearings 41 and 42 to the large diameter portion side while lubricating the tapered roller bearings 41 and 42 themselves. In that case, since the pinion shaft 51 of the front planetary gear mechanism 21 is disposed close to the side of the large diameter portion in the axial direction of the taper roller bearing 41 on the front planetary gear mechanism side, lubrication by the centrifugal action of the taper roller bearing 41 is performed. The oil supply direction and the disposition direction of the lubricating oil passage 54 of the pinion shaft 51 whose one end is open to the large diameter portion side of the tapered roller bearing 41 are substantially coincident with each other. The lubricating oil positively supplied from the side can be reliably guided to the bearing 53 for supporting the pinion gear via the lubricating oil passage 54 of the pinion shaft 51, and seizure of the bearing 53 for supporting the pinion gear can be prevented. be able to. In addition, the front planetary gear mechanism 2
Since the pinion shaft 51 of No. 1 has its tapered roller bearing side portion fixedly provided directly outside the loose fitting portion 5a of the intermediate gear 5, the support rigidity strength of the pinion shaft 51 is increased by the intermediate gear 5, and the front planetary gear Gear mechanism 2
The supporting rigidity strength of No. 1 can be improved.

The present invention is not limited to the above embodiment, but includes various other modifications.
For example, although the automatic transmission is used as the power transmission mechanism in the above embodiment, any mechanism may be used as long as the power is transmitted via the planetary gear mechanism.

In the above embodiment, the power transmission member is the intermediate gear 5, but it may be a converter output shaft.

[Brief description of drawings]

FIG. 1 is a cross-sectional view near a front planetary gear mechanism.

FIG. 2 is a skeleton diagram of the automatic transmission.

[Explanation of symbols]

 1 Automatic Transmission (Power Transmission Mechanism) 3 Transmission Case (Case) 5 Intermediate Gear (Output Gear) 41 Tapered Roller Bearing 21 Planetary Gear Mechanism 51 Pinion Shaft 52 Pinion Gear 53 Bearing 54 Lubricating Oil Path

Claims (2)

[Claims] 1. A power transmission member of a power transmission mechanism is supported by a case via a tapered roller bearing, and a pinion shaft of a planetary gear mechanism is arranged adjacent to a side of a large diameter portion in the axial direction of the tapered roller bearing. , The pinion shaft has one end open to the large diameter side of the tapered roller bearing and the other end opens near the bearing that supports the pinion gear on the pinion shaft, and lubricates from the large diameter side of the tapered roller bearing to the bearing. A lubricating structure for a planetary gear mechanism, which is provided with a lubricating oil passage for guiding oil. 2. The lubrication structure for a planetary gear mechanism according to claim 1, wherein the power transmission member is an output gear of the transmission, and the pinion shaft is supported by the output gear.