JP4606151B2 - Lubricating structure of planetary gear unit - Google Patents

Description

The present invention relates to a lubrication structure for a planetary gear device, and more particularly to a structure for lubricating a pinion gear or a needle bearing supported by a carrier.

Conventionally, a planetary gear device has been widely used as a forward / reverse switching mechanism for an automatic transmission or a continuously variable transmission. There are roughly two methods for lubricating the pinion gear of the planetary gear device. One method is a method of lubricating a pinion gear by providing a lubrication hole in a rotating member such as an input shaft, and flowing lubricating oil radially outward from the lubrication hole using centrifugal force. An oil supply hole in the radial direction is formed in the oil supply hole. Lubricating oil is supplied from the oil supply hole to the shaft center hole of the pinion shaft whose both ends are supported by the carrier. This is a method of lubricating the pinion gear.

The former method is a lubrication method using centrifugal force, and the oil passage structure is simple. However, when the carrier is stationary, the lubricant cannot be supplied to the pinion gear using the centrifugal force. There is a problem that the absolute amount of is insufficient. On the other hand, since the latter method is a forced lubrication method, the lubricating oil can always be supplied to the pinion gear, and there is no problem that the absolute amount of the lubricating oil is insufficient.

FIG. 9 shows an example of such a forced lubrication type planetary gear unit.
In FIG. 9, both ends of the pinion shaft 61 are supported by the carrier 60, and lubricating oil is supplied from the radial oil supply holes 62 provided in the carrier 60 to the axial hole 63 of the pinion shaft 61, Lubricating oil is guided to the outer peripheral surface of the pinion shaft 61 from the shaft center hole 63 to lubricate the pinion gear 64 and the needle bearing 65. In order to prevent the pinion shaft 61 from coming off from the carrier 60, a roller pin 66 is inserted from the outer peripheral side of the carrier 60, and the insertion portion is caulked 67. The open end side of the shaft hole 63 is sealed with a plug 68 to prevent the lubricating oil introduced to the shaft hole 63 from flowing out from the open end.

In the planetary gear device having the above-described structure, the lubricating oil is forcibly supplied from the oil supply hole 62 of the carrier 60 to the pinion gear 64 and the needle bearing 65 through the shaft center hole 63 of the pinion shaft 61. It can be surely prevented.
However, a roller pin 66 for preventing the pinion shaft 61 from coming off and a plug 68 for sealing the shaft center hole 63 are required, which not only increases the number of components, but also includes an operation for fixing the roller pin 66 by caulking and a plug 68. Mounting work is required, and the number of work steps increases. In particular, since three or more pinion shafts 61 are incorporated in one carrier 60, there is a disadvantage that the cost increases.

In Patent Document 1, a radial hole is formed in the carrier from the radially outer side, a locking tool for preventing the pinion shaft from being inserted is inserted into the radial hole, and a lubricating hole that intersects the shaft hole of the pinion shaft Has been proposed from the inside in the radial direction, and each radial hole is formed in a non-penetrating state. The open end side of the shaft hole of the pinion shaft is sealed with a plug.
In this case as well, a locking tool for retaining and a plug for sealing the shaft hole are necessary, and there are the same problems as described above.

In Patent Document 2, the pinion shaft is phase-matched to the carrier and welded so that the oil hole of the pinion shaft matches the oil hole of the carrier, and the open end of the shaft center hole of the pinion shaft is plugged. A planetary gear device having a sealed structure has been proposed.
In this case, there is no need for a pinion shaft retaining stopper and there is an advantage that the structure is simple. However, the pinion shaft and the carrier must be phase-matched and welded, Therefore, the work of accurately aligning and welding a plurality of pinion shafts is poor in workability and requires skill.
JP-A-6-201022 Japanese Utility Model Publication No. 7-19660

Accordingly, an object of the present invention is to provide a lubricating structure for a planetary gear device that eliminates the plug for sealing the axial hole of the pinion shaft, simplifies the assembly work, and reduces the number of components.

In order to achieve the above object, according to the first aspect of the present invention, lubricating oil is supplied from a radial oil supply hole provided in a carrier to an axial hole of a pinion shaft having both ends supported by the carrier. In the planetary gear device that guides lubricating oil from the shaft hole to the outer peripheral surface of the pinion shaft and lubricates the pinion gear, the shaft hole is formed in a non-penetrating state from one end side of the pinion shaft. is the formed on the end side with the first orthogonal hole non-through condition through the oil supply hole and the communicating of the carrier, the end portion of the pinion shaft of the open end side of the shaft Kokoroana, a larger diameter than the shaft Kokoroana A second orthogonal hole is formed in a non-penetrating state in a direction orthogonal to the axial hole, and is the same as the second orthogonal hole at a portion of the carrier that supports the open end side end of the axial hole of the pinion shaft. third orthogonal holes on diameter or is provided in a radial direction of the carrier, the 3 the inner periphery circumferential groove of the carrier perpendicular holes are opened is formed, the roller pin to the second orthogonal hole in the third orthogonal bore and the pinion shaft of the carrier by inserting the inner diameter side of the carrier, the at the same time closing the axial center hole of the pinion shaft with roller pins, by and retained the pinion shaft with respect to the carrier, mounting the snap ring in the circumferential groove, and characterized in that retaining the roller pin in the inner diameter direction A planetary gear device lubrication structure is provided.

In the present invention, the shaft center hole of the pinion shaft is a hole formed in a non-penetrating state from one end side of the pinion shaft, and communicates with the oil supply hole of the carrier at the terminal end side of the shaft center hole. Lubricating oil that has flowed radially outward is supplied from this portion to the axial hole of the pinion shaft. Roller pins are inserted into the third orthogonal hole of the carrier and the second orthogonal hole of the pinion shaft in order to prevent the lubricating oil supplied to the shaft hole from flowing out from the open end. These orthogonal holes are larger in diameter than the axial hole, and the roller pin is also larger in diameter than the axial hole, so that the open end can be reliably sealed. The roller pin also has a function of preventing the pinion shaft from coming off from the carrier.
In the present invention, the roller pin refers to all cylindrical parts, and is not limited to a solid part but may be a hollow part. Since it is inserted into the second and third orthogonal holes with almost no gap and is larger in diameter than the axial hole, the axial hole can be reliably sealed at a portion orthogonal to the axial hole, from the open end of the axial hole. Lubricating oil can be prevented from leaking.
Further, the third orthogonal hole of the carrier may have the same diameter as or larger than the second orthogonal hole of the pinion shaft.

In the present invention, a circumferential groove is formed in the inner circumferential portion of the carrier where the third orthogonal hole is opened, and the roller pin is prevented from coming off in the inner diameter direction by attaching a snap ring to the circumferential groove.
In this case, by attaching the snap ring, the roller pin is prevented from coming off, so that it is not necessary to caulk the carrier, and moreover, a plurality of roller pins can be prevented from coming off by one snap ring, so that the assembling workability is improved.

As described above, according to the present invention, since the roller pin serves as both sealing of the pinion shaft shaft hole and retaining of the pinion shaft, the plug for sealing the pinion shaft shaft hole can be eliminated, Assembly work is simplified and the number of parts can be reduced. Particularly, since it is necessary to assemble a plurality of pinion shafts with respect to one carrier, the lubricating structure of the present invention is more effective.

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

1 to 3 show an example of a continuously variable transmission using a planetary gear device as a premise of the present invention.
The continuously variable transmission of this embodiment is an FF horizontal type automobile transmission, which is roughly switched between forward and reverse rotation of the input shaft 3 driven by the engine output shaft 1 via the torque converter 2 and the input shaft 3. The forward / reverse switching mechanism 4 that transmits to the drive shaft 10, the continuously variable transmission A that includes the drive pulley 11, the driven pulley 21, and the V-belt 15 that is wound between the pulleys, and the output shaft 32 And a differential device 30 that transmits to the terminal. The input shaft 3 and the drive shaft 10 are arranged on the same axis, and the driven shaft 20 and the output shaft 32 of the differential device 30 are arranged parallel to the input shaft 3 and non-coaxially. Therefore, this continuously variable transmission has a three-axis configuration as a whole.
The V belt 15 used in this embodiment is a known metal belt composed of a pair of endless tension bands and a large number of blocks supported by these tension bands.

Each component constituting the continuously variable transmission is accommodated in a transmission case 5. An oil pump 6 is disposed between the torque converter 2 and the forward / reverse switching mechanism 4. As shown in FIG. 3, the oil pump 6 includes an oil pump body 7 fixed to the transmission case 5, an oil pump cover 8 fixed to the oil pump body 7, an oil pump body 7, and an oil pump. A pump gear 9 accommodated between the cover 8 and the cover 8 is used. The pump gear 9 is driven by the pump impeller 2 a of the torque converter 2. The turbine runner 2b of the torque converter 2 is connected to the input shaft 3, and the stator 2c is supported by the transmission case 5 via the one-way clutch 2d.

As shown in FIG. 3, the forward / reverse switching mechanism 4 includes a planetary gear device 40, a reverse brake 50, and a direct coupling clutch 51, and a sun gear 41 of the planetary gear device 40 is connected to the input shaft 3 that is an input rotation member. The ring gear 42 is connected to the drive shaft 10 which is an output rotating member. The planetary gear device 40 is a single pinion system, the reverse brake 50 is provided between the carrier 44 supporting the pinion gear 43 and the transmission case 5, and the direct clutch 51 is provided between the carrier 44 and the sun gear 41. . When the direct clutch 51 is released and the reverse brake 50 is engaged, the rotation of the input shaft 3 is reversed and decelerated and transmitted to the drive shaft 10. On the contrary, when the reverse brake 50 is released and the direct clutch 51 is engaged, the carrier 44 and the sun gear 41 of the planetary gear device 40 rotate together, so that the input shaft 3 and the drive shaft 10 are directly connected.

The piston 50b of the reverse brake 50 is accommodated in a concave hydraulic chamber 50c formed on the inner wall of the transmission case 5 as shown in FIG. 3, and the piston 50b is operated by the hydraulic pressure supplied to the hydraulic chamber 50c. Fasten the brake disc 50a. The end of the brake disc 50a pushed by the pressure of the piston 50b is supported by a cylindrical protrusion 8a protruding from an oil pump cover 8 that is a stationary member.

As shown in FIG. 3, a cylindrical portion 41a serving as a clutch hub of the direct coupling clutch 51 is integrally projected on the front side (engine side) of the sun gear 41, and a clutch disk of the direct coupling clutch 51 is provided on the outer periphery of the cylindrical portion 41a. The inner diameter portion of 51a is supported. A concave hydraulic chamber 51b is formed on the side of the oil pump cover 8 on the back side (forward / reverse switching mechanism side). The piston 51c is operated by the hydraulic pressure supplied to the hydraulic chamber 51b, and the direct clutch 51 is fastened. . The piston 51c has a U-shaped cross section, and a thrust bearing 52 that allows relative rotation is attached to a side surface of the piston 51c that faces the clutch disk 51a. Therefore, the axial pressure of the piston 51c is effectively transmitted to the clutch disk 51a, and the piston 51c is prevented from rotating with the clutch disk 51a of the direct coupling clutch 51. Since the carrier 44 (carrier rim 46) is arranged behind the clutch disk 51a, the end of the clutch disk 51a pushed by the piston 51c is supported by the end surface of the carrier 44 (side surface of the carrier rim 46). Can do.

The drive pulley 11 of the continuously variable transmission A is integrally movable with a fixed sheave 11a integrally formed on a drive shaft (pulley shaft) 10 and axially movable on the drive shaft 10 via a roller spline portion 13. The movable sheave 11b is rotatably supported, and the hydraulic servo 12 is provided behind the movable sheave 11b. A piston portion 12a extending to the back side is integrally formed on the outer peripheral portion of the movable sheave 11b, and the outer peripheral portion of the piston portion 12a is in sliding contact with the inner peripheral portion of the cylinder 12b fixed to the drive shaft 10. A hydraulic oil chamber 12c of the hydraulic servo 12 is formed between the movable sheave 11b and the cylinder 12b, and the shift control is performed by controlling the hydraulic pressure to the hydraulic oil chamber 12c.

The driven pulley 21 is supported by a fixed sheave 21a integrally formed on the driven shaft (pulley shaft) 20 and on the driven shaft 20 via a roller spline portion 23 so as to be axially movable and integrally rotatable. A movable sheave 21b and a hydraulic servo 22 provided behind the movable sheave 21b are provided. The structure of the roller spline portion 23 is the same as that of the roller spline portion 13 of the drive pulley 11. A cylinder portion 22a extending to the rear side is integrally formed on the outer peripheral portion of the movable sheave 21b, and a piston 22b fixed to the driven shaft 20 is in sliding contact with the inner peripheral portion of the cylinder portion 22a. A hydraulic oil chamber 22c of the hydraulic servo 22 is formed between the movable sheave 21b and the piston 22b. By controlling the hydraulic pressure of the hydraulic oil chamber 22c, belt thrust necessary for torque transmission is given. Note that a spring 24 for applying an initial thrust is disposed in the hydraulic oil chamber 22c.

One end of the driven shaft 20 extends toward the engine side, and an output gear 27a is fixed to this one end. The output gear 27a meshes with the ring gear 31 of the differential device 30, and power is transmitted from the differential device 30 to the output shaft 32 extending left and right to drive the wheels.

In the continuously variable transmission configured as described above, at the time of forward movement, the reverse rotation brake 50 is engaged and the direct coupling clutch 51 is released, whereby the driving force input from the torque converter 2 is reversed and decelerated and transmitted to the driving pulley 11. The Then, the output shaft 32 is driven in the same direction as the engine rotation direction via the driven pulley 21 and the differential device 30. At the time of forward movement, the reverse brake 50 is engaged, so that the carrier 44 is stationary.
On the other hand, at the time of reverse travel, by engaging the direct coupling clutch 51 and releasing the reverse brake 50, the input side (sun gear 41) and the output side (ring gear 42) of the planetary gear device 40 are directly coupled. The drive force thus transmitted is transmitted to the drive pulley 11 as it is, and the output shaft 32 is driven in the direction opposite to the engine rotation direction via the driven pulley 21 and the differential device 30.

Here, the lubricating structure of the planetary gear device 40 will be described with reference to FIGS.
The carrier 44 is composed of a disk-shaped carrier flange 45 and an annular carrier rim 46, and the inner diameter portion of the carrier flange 45 extends in the inner diameter direction between the sun gear 41 and the ring gear 42, and is rotatable about the input shaft 3. It is supported by. The carrier flange 45 is integrally formed with a plurality of (here, six) columnar portions 45a protruding in the axial direction toward the carrier rim 46, and the pinion gear 43 is disposed in a space between the columnar portions 45a. . The front end surface of the columnar portion 45a and the carrier rim 46 are metal-bonded by sintering, and the carrier flange 45 and the carrier rim 46 are integrally fixed. It may be fixed by welding, brazing, screwing or the like.

A lubrication hole 3 a opened at the shaft end is formed in the shaft center of the input shaft 3. As shown in FIG. 5, a bush 35 is press-fitted into the inner diameter portion of the carrier flange 45, and the inner peripheral surface of the bush 35 is rotatably fitted to the shaft end portion of the input shaft 3. A diameter-enlarged portion 45b that is expanded in the axial direction is formed on the inner diameter portion of the carrier flange 45, and a closing member 36 that closes the diameter-enlarged portion 45b is fitted. A plurality of (for example, six) inflow grooves 45c are formed in the inner peripheral surface of the carrier flange 45 and in contact with the outer peripheral surface of the bush 35 in the axial direction at intervals in the circumferential direction. The groove 45 c communicates with a radial oil supply hole 45 d formed inside the carrier flange 45. Since the lubricating oil sent through the lubricating hole 3a of the input shaft 3 is prevented from flowing out in the axial direction by the plugging member 36, an oil reservoir is formed inside the enlarged diameter portion 45b. Therefore, the lubricating oil is fed into the oil supply hole 45d through the inflow groove 45c by the lubricating pressure of the oil reservoir.

As shown in FIG. 7, bearing holes 45e and 46a are formed at the opposing positions of the carrier flange 45 and the carrier rim 46, and both ends of the pinion shaft 47 for supporting the pinion gear 43 are bridged between these bearing holes 45e and 46a. Inserted. Thrust washers 37 are disposed between the pinion gear 43 and the carrier flange 45 and between the pinion gear 43 and the carrier rim 46, respectively. A needle bearing 38 is disposed in the gap between the inner periphery of the pinion gear 43 and the outer periphery of the pinion shaft 47, and the pinion gear 43 is rotatable with respect to the pinion shaft 47. The pinion shaft 47 is formed with a non-penetrating shaft center hole 47a from the end on the carrier rim 46 side. The radial hole 47b provided on the terminal end side of the shaft center hole 47a is connected to the carrier flange 45. It communicates with the formed radial oil supply hole 45d. The lubricating oil supplied to the shaft hole 47a is guided to the outer peripheral surface of the pinion shaft 47 from the radial hole 47c, and can lubricate the pinion gear 43, the needle bearing 38, the thrust washer 37, and the like.

The carrier rim 46 is integrally formed with a cylindrical portion 46b that protrudes in the axial direction toward the front side (engine side). The cylindrical portion 46b connects the brake hub of the reverse brake 50 and the clutch drum of the direct clutch 51. Also serves as. That is, a spline portion 46c that engages with the inner diameter portion of the brake disc 50a of the reverse brake 50 is formed on the outer peripheral portion of the cylindrical portion 46b, and the outer diameter portion of the clutch disc 51a of the direct coupling clutch 51 is engaged with the inner peripheral portion. A spline portion 46d is formed.

As shown in FIG. 7, at one end of the pinion shaft 47 supported by the carrier rim 46, that is, at the end of the pinion shaft 47 on the open end side of the shaft center hole 47a, an orthogonal hole larger in diameter than the shaft center hole 47a. 47d is formed in a direction orthogonal to the axial hole 47a. The carrier rim 46 is formed with an orthogonal hole 46e having the same diameter or more as the orthogonal hole 47d. When the roller pin 48 is inserted into the orthogonal holes 46e and 47d, the phase of the radial hole 47b formed in the pinion shaft 47 and the oil supply hole 45d formed in the carrier flange 45 can be automatically matched. Then, by forming the caulking 46f in the opening portion of the orthogonal hole 46e of the carrier rim 46, the roller pin 48 can be reliably prevented from coming off. Since the diameter of the roller pin 48 is larger than that of the shaft hole 47a, the open end of the shaft hole 47a can be reliably sealed, and the lubricating oil supplied to the shaft hole 47a can be prevented from flowing out from the open end. In this way, by inserting the roller pin 48 into the orthogonal holes 46e and 47d, the pinion shaft 47 can be fixed at the same time as the shaft hole 47a of the pinion shaft 47 is sealed with the roller pin 48.

Since the reverse brake 50 is engaged in the forward range, the carrier 44 (45, 46) is stationary. For this reason, the lubricating oil cannot be supplied to the pinion gear 43 using centrifugal force, and problems such as wear of the pinion gear 43 and seizure of the needle bearing 38 may occur. In this embodiment, since the lubricating oil sent through the lubricating hole 3 a of the input shaft 3 is prevented from flowing out in the axial direction by the plugging member 36, an oil reservoir is formed inside the plugging member 36. Therefore, the lubricating oil is fed into the oil supply hole 45d by the lubricating pressure of the oil reservoir, and is further supplied to the shaft center hole 47a of the pinion shaft 47. Since the open end of the shaft hole 47a is sealed by the roller pin 48, oil leakage from the open end can be prevented. Therefore, the lubricating oil supplied to the shaft hole 47a can lubricate the needle bearing 38, the pinion gear 43, the thrust washer 37, and the like. Thus, even if the carrier 44 is stationary during the forward range, the needle bearing 38 and the pinion gear 43 can be effectively prevented from being worn or seized.

In the above embodiment, since the orthogonal hole 46e of the carrier rim 46 is formed from the outside in the radial direction, the roller pin 48 can be easily prevented from coming off by performing the caulking 46f after inserting the roller pin 48. The orthogonal hole 46e is not limited to being formed from the radially outer side, but may be formed from the radially inner side.
In the above embodiment, the tip of the roller pin 48 passes through the pinion shaft 47 and ends at the inner surface of the bearing hole 46a. 46 may extend to the inside. In short, it is only necessary that the roller pin 48 is inserted to a depth that can seal the shaft hole 47a.

FIG. 8 shows a first embodiment of the present invention.
In this embodiment, the orthogonal hole 46e of the carrier rim 46 is opened to the inner diameter side of the carrier rim 46, and the roller pin 48 is inserted into the orthogonal hole 46e and the orthogonal hole 47d of the pinion shaft 47 through this opening. A circumferential groove 46g is formed in the opening of the orthogonal hole 46e, and a snap ring 39 is attached to the circumferential groove 46g to prevent the roller pin 48 from coming off. Since the snap ring 39 has a spring force extending in the radial direction, the snap ring 39 does not fall off the circumferential groove 46g.

In this embodiment, by attaching the snap ring 39, the roller pin 48 can be prevented from coming off in the inner diameter direction, so that it is not necessary to crimp the carrier rim 46, and the assembling work is simplified. In particular, since the number of roller pins 48 required is the same as the number of pinion shafts 47, three or more roller pins 48 are required for one carrier 44 (45, 46). Since it can be retained at 39, the working efficiency is greatly improved.

In the above embodiment, the planetary gear device of the present invention is applied to a continuously variable transmission. However, if the planetary gear device of a forced lubrication system is provided, it can be applied to a general automatic transmission. Of course.
Moreover, although the cylindrical part 46b which serves as a brake hub and a clutch drum was provided in the carrier rim 46 which comprises a carrier, the carrier which does not have such a cylindrical part may be sufficient.
Furthermore, the carrier 44 is not limited to the two parts of the carrier flange 45 and the carrier rim 46 but may be an integral structure.

It is an expanded sectional view of an example of a continuously variable transmission using a planetary gear set which is a premise of the present invention. FIG. 2 is a skeleton diagram of the continuously variable transmission shown in FIG. 1. It is a detailed sectional view of the forward / reverse switching mechanism shown in FIG. It is a front view of a planetary gear device. It is the VV sectional view taken on the line of FIG. FIG. 6 is a cross-sectional view taken along line VI-VI in FIG. 5. It is a principal part enlarged view of FIG. It is sectional drawing of 1st Example of the planetary gear apparatus of this invention. It is sectional drawing of an example of the conventional planetary gear apparatus.

Explanation of symbols

3 Input shaft 3a Lubrication hole 37 Thrust washer 38 Needle bearing 39 Snap ring 40 Planetary gear unit 41 Sun gear 42 Ring gear 43 Pinion gear 44 Carrier 45 Carrier flange 45d Oil supply hole 46 Carrier rim 46e Orthogonal hole 46f Caulking 46g Circumferential groove 47 Pinion shaft 47a Shaft Core hole 47d Right angle hole 48 Roller pin

Claims (1)

Lubricating oil is supplied from the radial oil supply hole provided in the carrier to the shaft hole of the pinion shaft supported at both ends of the carrier, and the lubricating oil is guided from the shaft hole to the outer peripheral surface of the pinion shaft. In a planetary gear unit that lubricates a pinion gear,
The axial hole is formed in a non-penetrating state from one end side of the pinion shaft,
A first orthogonal hole communicating with the oil supply hole of the carrier is formed in a non-penetrating state on the terminal end side of the shaft hole;
A second orthogonal hole having a larger diameter than the axial hole is formed in a non-penetrating state in a direction orthogonal to the axial hole at the end of the pinion shaft on the open end side of the axial hole.
The site of the carrier for supporting the open end side end portion in the axial hole of the pinion shaft, the third orthogonal holes on the second orthogonal hole the same diameter or is provided in a radial direction of the carrier,
A circumferential groove is formed in the inner peripheral portion of the carrier where the third orthogonal hole opens,
By inserting the roller pin to the second orthogonal hole in the third orthogonal bore and the pinion shaft of the carrier from the inner diameter side of the carrier, at the same time closing the axial bore of the pinion shaft in the roller pins, the pinion shaft to the carrier Against it ,
A lubricating structure for a planetary gear device , wherein a snap ring is attached to the circumferential groove to prevent the roller pin from coming off in an inner diameter direction .

Images