JPH0632816U - Lubrication structure of planetary gear mechanism - Google Patents

Abstract

(57) [Abstract] [Purpose] To reduce the number of parts by improving the existing members so that lubricating oil can be reliably supplied to the bearings for supporting the pinion gears even if an oil path is not required. It is in. [Structure] Pinion shaft 22e of rear planetary gear mechanism 22
The bearing for supporting the pinion gear from one side
As a lubrication structure of a planetary gear mechanism provided with a lubricating oil passage 46 for guiding lubricating oil up to 41, a front pinion carrier 53 and an orthogonal portion of a coupling member 54 facing the front pinion carrier 53.
54a, the thrust bearing 55 is arranged, the inner race 55a of the thrust bearing 55 is extended radially outward, and the portion of the extended portion corresponding to the one end opening of the lubricating oil passage 46 is extended radially. A guide member 56 is configured to be projected to the side of the orthogonal portion 54a of the coupling member 54 over the entire circumference in the direction to guide the supply of the lubricating oil into the lubricating oil passage 46 from one side surface side of the pinion shaft 22e.

Description

[Detailed description of the device]

[0001]

[Industrial applications]

 The present invention relates to a lubrication structure of a planetary gear mechanism, and more particularly to a lubrication measure for a bearing that supports a pinion gear on a pinion shaft.

[0002]

[Prior art]

 Conventionally, in a power transmission mechanism such as a transmission, a driving force (rotational force) from a power transmission shaft rotatably supported in the case of the power transmission mechanism is transmitted to a planetary gear mechanism arranged on the shaft. It is designed to output after appropriately changing it by changing the path.The lubrication for such a planetary gear mechanism is performed by the oil sprinkled by centrifugal force through a hole opening in the oil passage in the power transmission shaft. It has been done.

In that case, one end is used as a measure against lubrication for a portion which is difficult to be supplied with the oil sprinkled by the centrifugal force as described above, particularly for a bearing for rotatably supporting the pinion gear on the pinion shaft of the planetary gear mechanism. The pinion shaft is opened on one side and the other end is opened near the bearing to provide a lubricating oil passage for guiding the lubricating oil from one side of the pinion shaft to the bearing, and one side of the pinion shaft By providing an oil path on the side that receives and stores the oil (lubricating oil) sprinkled by centrifugal force, the bearings for supporting the pinion gears can be lubricated with sufficient lubricating oil in the oil path. It is known (see Japanese Utility Model Laid-Open No. 58-67161).

Further, a thrust bear ring is arranged between the pinion carrier of the planetary gear mechanism and another power transmission member facing one side surface of the pinion shaft with respect to the pinion carrier.

[0005]

[Problems to be solved by the device]

 However, the above-described bearings for supporting the pinion gears, which are provided with lubrication measures, have a drawback that an additional oil path is required on one side surface of the pinion shaft, which increases the number of parts.

The present invention has been made in view of the above points, and it is an object of the present invention to eliminate the need for an oil path and to improve the existing members so that lubricating oil can be reliably supplied to bearings for supporting pinion gears. In this way, the number of parts can be reduced.

[0007]

[Means for Solving the Problems]

 In order to achieve the above-mentioned object, a solution provided by the present invention is a pinion shaft of a planetary gear mechanism, in which one end is opened at one side surface of the pinion shaft and the other end is opened near a bearing that supports the pinion gear in a pinion shaft. Then, it is assumed that the lubrication structure of the planetary gear mechanism is provided with a lubricating oil passage for guiding the lubricating oil from one side of the pinion shaft to the bearing. A thrust bearing is disposed between the pinion carrier of the planetary gear mechanism and another power transmission member facing one side surface of the pinion shaft with respect to the pinion carrier. The race on the side of the pinion carrier is extended outward in the radial direction, and the extended portion is formed as an internal member for guiding the lubricating oil into the lubricating oil passage from one side of the pinion shaft. It is a thing.

[0008]

[Action]

 With the above structure, in the present invention, the lubricating oil sprinkled by the centrifugal force of the power transmission shaft is guided to the thrust bearing from the radially inner side of the pinion carrier through the pinion gears of the planetary gear mechanism. , The race on the pinion carrier side of this thrust bearing is stored in an extended portion, that is, a guide member, that extends radially outward, and the lubricating oil is supplied and guided into the lubricating oil passage that opens to one side surface of the pinion shaft. This means that the lubricating oil can be reliably guided to the bearing for supporting the pinion gear through the lubricating oil passage without providing an additional oil path on one side surface of the pinion shaft.

[0009]

As described above, according to the lubrication structure of the planetary gear mechanism according to the present invention, the lubricating oil sprinkled by the centrifugal force of the power transmission shaft is stored in the guide member of the race on the pinion carrier side of the thrust bearing. Since the supply is guided from one side of the pinion shaft into the lubricating oil passage, the oil path on the one side of the pinion shaft is not required, but the supply of lubricating oil to the bearing for supporting the pinion gear through the lubricating oil passage is ensured. Therefore, the number of parts can be reduced.

[0010]

【Example】

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

FIG. 3 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 includes a torque converter 10 and a torque converter 10 on the same axis. And a sub transmission 30 arranged on an axis parallel to these axes.

The torque converter 10 includes a pump 12 that is integrated in a case 11 that is connected to the engine output shaft 2, and a turbine 13 that is disposed opposite to the pump 12 and that is driven by the pump 12 via hydraulic oil. , A stator 15 arranged between the pump 12 and the turbine 13 and supported by the transmission case 3 via a one-way clutch 14, a converter output shaft 16 connected to the turbine 13, and the case 1 The lockup clutch 17 connects the converter output shaft 16 directly to the engine output shaft 2 via the lockup clutch 17.

An oil pump 4 driven by the engine output shaft 2 via the torque converter 10 is arranged between the torque converter 10 and the main transmission 20.

The main transmission 20 has a front planetary gear mechanism 21 arranged on the converter output shaft 16 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 to the sun gear 22a of the rear planetary gear mechanism 22 via the direct coupling clutch 24. In addition, 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.

A first one-way clutch 25 and a low reverse brake 26 are arranged in parallel between the ring gear 21 b of the front planetary gear mechanism 21 and the transmission case 3, and the rear planetary gear mechanism 22 includes 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. There is. Then, the pinion carriers 21c, 22c of the front planetary gear mechanism 21 and the rear planetary gear mechanism 22 are coupled, and the intermediate gear 5 as an output gear for transmitting power from the main transmission 20 to the sub transmission 30 is coupled to these. Has been done.

With this configuration, according to the main transmission 20, the forward clutch 23, the direct coupling clutch 24, the 3-4 brake 28, and the low reverse brake 26 are selectively engaged, so that the low speed stage of forward traveling is reduced. Therefore, the middle and high speed stages and the reverse stage will be obtained.

On the other hand, the sub transmission 30 has a single planetary gear mechanism 31, and the intermediate gear 6 that is always meshed with the intermediate gear 5 in the main transmission 20 is connected to the ring gear 31 a of the planetary gear mechanism 31. A direct coupling clutch 32 is arranged between the ring gear 31a 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. It is located in. The output gear 7 is connected to the pinion carrier 31c of the planetary gear mechanism 31, and power is transmitted from the gear 7 to the left and right drive wheels (not shown) via a differential device.

The sub-transmission 30 can shift the dynamic force input from the main transmission 20 via the intermediate gears 5 and 6 to two forward speeds, a low speed step and a high speed step, and output it to the output gear 7. You can do it.

That is, when the direct coupling clutch 32 is released, the sun gear 31 b of the planetary gear mechanism 31 is fixed to the ring gear 31 a of the planetary gear mechanism 31 by the third one-way clutch 33 or the reduction brake 34. The input power from the intermediate gear 6 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 engine brake will operate as the auxiliary transmission 30 alone.

When the direct coupling clutch 32 is engaged and the deceleration brake 34 is released, the ring gear 31a of the planetary gear mechanism 31 and the sun gear 31b are coupled to each other, so that the power from the intermediate gear 6 is generated. Is output from the pinion carrier 31c to the output gear 7 as it is, whereby a high speed stage (direct connection stage) is obtained.

In this way, the main transmission 20 can obtain three forward gears and one reverse gear, and the auxiliary transmission 30 can form two high and low gears with respect to the output of the main transmission 20. Therefore, as a whole, the automatic transmission can obtain 6 shift stages for forward movement, and for reverse movement, the reverse stage of the main transmission 20 and the deceleration brake 34 of the auxiliary transmission 30 are engaged. By combining with the set low speed stage, the reverse stage as a whole can be obtained. Further, in this embodiment, 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 the respective shift speeds of the forward 5 speeds and the reverse 1 speed are summarized in Table 1. It should be noted that in Table 1, the mark ● indicates that only the range for the engine brake is engaged.

[0023]

[Table 1] In this embodiment, as shown in FIG. 1, in the rear planetary gear mechanism 22 (the front planetary gear mechanism 21 also has the same configuration, only the rear planetary gear mechanism 22 shown in the figure will be described), the pinion gear 22d thereof will be described. A bearing 41 for supporting the pinion shaft 22e so as to be rotatable relative to the pinion shaft 22e is provided. Further, the converter output shaft 16 is provided with an oil passage 42 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. Are provided so as to communicate with the oil passage 42 by penetrating therethrough, and one of the communication holes 43, ... Corresponds to the rear planetary gear mechanism 22.

Further, the substantially tubular coupling member 44 that couples the sun gear 22 a of the rear planetary gear mechanism 22 and the second one-way clutch 27 has a plurality of through holes 45 (FIG. Is shown). Then, one end of the above-mentioned pinion shaft 22e is opened at one side surface (right side in the figure) of the pinion shaft 22e and extends in the axial direction of the pinion shaft 22e, and then the diameter of the bearing 41 from a central portion in the axial direction of the bearing 41 is increased. A lubricating oil passage 46 is provided which extends radially in the direction and has the other end opened to the bearing 41 to guide the lubricating oil from one side surface of the pinion shaft 22e to the bearing 41.

Also, as shown in FIG. 2, the pinion carrier 22c supports a plurality of pinion gears 22d (only two positions are shown in the drawing) from the rear side in the engine direction (left side in the drawing) which is the other side surface side. The rear side pinion carrier supports the pinion gear 22d and the bearing 41 via a bearing 51. On the other hand, a front side pinion carrier 53 that supports each pinion gear 22d from the front side in the engine direction is provided on the front side in the engine direction (right side in the figure), which is one side surface of the pinion gear 22d, and the front pinion carrier 53 is provided. Also supports the pinion gear 22d and the bearing 41 via the bearing 51. A plurality of holes 52 are formed between the rear pinion carrier 22c (pinion carrier 22c) and the front pinion carrier 53 where the pinion gear 22d is not located, that is, between the pinion gears 22d. Further, a coupling member 54 as another power transmission member that couples the sun gear 21a of the front planetary gear mechanism 21 and the ring gear 22a of the rear planetary gear mechanism 22 is orthogonal to the axis of the converter output shaft 16. The cross section 54a has a cross section 54a. The cross section 54a is arranged to face the front pinion carrier 53. Further, a thrust bearing 55 is arranged between the front pinion carrier 53 and the orthogonal portion 54a of the coupling member 54. Of the pair of races 55a and 55b of the thrust bearing 55 which are rotatable relative to each other, the inner race 55a located on the front pinion carrier 53 side extends radially outward. In the extending portion of the inner race 55a, a portion corresponding to the one end opening of the lubricating oil passage 46 projects to the orthogonal portion 54a side of the coupling member 54 over the entire circumference in the radial direction, and the front and rear pinion carriers 53 are provided. , 22c is configured as a guide member 56 for guiding the lubricating oil guided through the holes 52 of the pinion shaft 22e into the lubricating oil passage 46 from one side surface of the pinion shaft 22e.

Therefore, in the above-described embodiment, the lubricating oil sprinkled from the oil passage 43 through the communication holes 44, 44 by the centrifugal force of the converter output shaft 16 causes the lubricating oil to move to the rear as shown by the arrow in FIG. After being guided from the radially inner side of the front and rear pinion carriers 53, 22c through the holes 52 through the pinion gears 22d of the planetary gear mechanism 22, the thrust bearing 55 is extended to the extending portion of the inner race 55a of the thrust bearing 55. The lubricating oil is accumulated by the guide member 56 that projects the portion corresponding to the one-end opening of the lubricating oil passage 46, which extends to the orthogonal portion 54a side of the coupling member 54 over the entire circumference in the radial direction, and the lubricating oil is stored in the pinion shaft 22e. The lubricating oil is supplied and guided from the one side surface into the lubricating oil passage 46, and the lubricating oil is supplied to the pinion shaft without providing an additional oil path on one side surface of the pinion shaft. It can be surely guided to the bearing 41 for supporting the pinion gear via the lubricating oil passage 46 of 2e, and the number of parts can be reduced.

In the above embodiments, the planetary gear mechanism applied to the automatic transmission has been described, but it goes without saying that it can be applied to the planetary gear mechanism of any power transmission device.

[Brief description of drawings]

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

FIG. 2 is an exploded perspective view of a pinion gear and a thrust bearing between pinion carriers.

FIG. 3 is a skeleton diagram of the automatic transmission.

[Explanation of symbols]

 22 Rear planetary gear mechanism (planetary gear mechanism) 22d Pinion gear 22e Pinion shaft 41 Bearing 46 Lubricating oil passage 53 Rear side pinion carrier (pinion carrier) 54a Cross section of connecting member (other power transmission member) 55 Thrust bearing 55a Inner race ( Race) 56 Guide member

Claims (1)

[Scope of utility model registration request] 1. A pinion shaft of a planetary gear mechanism, one end of which is opened on one side of a pinion shaft and the other end of which is opened near a bearing that supports a pinion gear on the pinion shaft, from one side of the pinion shaft to the bearing. In a lubrication structure of a planetary gear mechanism provided with a lubricating oil passage for guiding a lubricating oil, a pinion carrier of the planetary gear mechanism and another power that opposes the pinion carrier on one side of the pinion shaft. A thrust bearing is arranged between the transmission member and a race of the thrust bearing on the side of the pinion carrier is extended outward in the radial direction, and the extended portion is formed on one side surface of the pinion shaft. Lubricating structure of planetary gear mechanism, characterized in that it is formed as a guide member for guiding the lubricating oil into the lubricating oil passage from the side .