JPH0689816B2 - Forced lubricator for planetary gears - Google Patents

Description

Description: TECHNICAL FIELD The present invention relates to a forced lubrication device for a planetary gear device in an automatic transmission.

[Conventional technology]

An automatic transmission changes gears by changing the power transmission path by connecting and disengaging the speed change elements of a plurality of planetary gear devices by engaging and releasing friction engagement elements. The pinion gear that constitutes the gear is a gearshift element that frequently rotates at a high speed because the pinion gear is rotatably driven to transmit power when the vehicle equipped with the automatic transmission is traveling, except when in a direct connection state. For this reason, the conventional pinion gear is rotatably supported on the pinion shaft by disposing a roller bearing or the like on the inner periphery thereof, and both axial side surfaces of the pinion gear are in contact with a shaft support portion supporting the pinion shaft via a thrust washer. A structure is adopted in which both the thrust washer and the roller bearing are lubricated by the oil that is supported and released from the oil passage provided in the sun gear on the inner circumference of the pinion gear and the inner circumference of the speed change shaft as the speed change shaft rotates. ing.

In the lubrication method as described above, the bearings arranged between the pinion gear and the pinion shaft are lubricated using the oil supplied to the thrust washer, so the bearings in the rotation support part are sufficiently supplied with oil. There is a problem that cannot be understood. Therefore, it is not unthinkable to provide a dedicated oil passage in the shaft support part, but as is known, there is a demand for compactness in the automatic transmission, and both axial length and outer diameter are possible. It is designed to be as compact as possible, and on the other hand, it is said that the arrangement of the mechanism inside the transmission is closely arranged due to the requirement of multiple stages. Since the shaft support portion is also made thin due to such requirements, it is impossible to form an oil passage in the shaft support portion.

Under these circumstances, the pinion shaft is provided with an oil passage in the shaft that communicates the axial end surface on the shaft support portion side with the outer peripheral surface, and the oil released from the oil passage of the speed change shaft is provided separately from the lubrication of the thrust washer. In order to supply the oil to the oil port on the axial end surface side of the oil passage in the shaft, a lubricating means has been proposed in which an oil reservoir is attached to the side surface of the shaft support portion and the rotation support portion of the pinion gear is forcibly lubricated. 58-67161
(See the official gazette).

[Problems to be solved by the invention]

By the way, in the above-mentioned lubrication means, oil is supplied from the center side between the shaft support portion and a member arranged adjacent to the shaft support portion, and the oil reservoir opening is provided between the shaft support portion and the adjacent member. Although it is flowing in,
In such a configuration, the lubricating oil may flow from the gap between the oil reservoir and the adjacent member and may not be sufficiently supplied into the opening of the oil reservoir.

Therefore, the present invention utilizes the thrust bearing interposed between the shaft support portion and the member disposed adjacent to the shaft support portion as a guide to ensure sufficient supply of lubricating oil to the oil reservoir. It is an object of the present invention to secure and solve the problem of insufficient lubrication of the transmission gear rotation support bearing in the automatic transmission.

[Means for solving problems]

To achieve the above object, the present invention has a ring gear, a pinion gear, a sun gear, a pinion shaft that rotatably supports the pinion gear via bearings, and a carrier that supports the pinion shaft. A planetary gear device, an outer peripheral discharge oil passage formed on the shaft, and a shaft internal oil formed from the axial end of the pinion shaft toward the inside of the shaft to guide lubricating oil from the outer peripheral discharge oil passage to the bearing. And an oil reservoir provided at an axial end of the pinion shaft for guiding lubricating oil to an oil passage in the shaft, a forced lubrication device of a planetary gear device, wherein an inner periphery of the oil reservoir has an axis of the pinion shaft. A guide portion that is bent in a direction away from the end is formed, and a guide portion that is radially inward of the oil reservoir and of the outer peripheral discharge oil passage is formed. A thrust bearing that restricts the axial movement of the planetary gear device is disposed on the outer side in the direction, and a bent portion that is bent in the axial direction toward the pinion shaft support portion side is formed on the outer periphery of the thrust trace of the thrust bearing. The guide part and the bent part are overlapped in the axial direction.

[Operation and effect of the invention]

In the forced lubrication device according to the present invention configured as described above, the lubricating oil discharged from the outer peripheral discharge oil passage formed in the shaft of the planetary gear device along with the rotation of the shaft passes through the thrust bearing to the outer peripheral side. And is guided to the bent portion of the thrust trace that overlaps the guide portion of the oil reservoir and is reliably introduced into the oil reservoir. The oil introduced into the oil reservoir flows into the oil passage in the shaft, reaches the bearing through the oil passage, and lubricates the bearing with a sufficient amount of oil.

Therefore, this forced lubrication device functions extremely effectively when applied to a planetary gear device in which the planetary gear rotates at a high speed while the sun gear is stopped.

〔Example〕

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

FIG. 1 is a sectional view showing a main part of an automatic transmission to which a forced lubrication device according to an embodiment of the present invention is applied, and FIG. 2 is a sectional view showing the whole thereof.

As shown in FIG. 2, the automatic transmission 100 includes a hydraulic torque converter 200, a transmission 300, and a hydraulic control device 400.

The transmission 300 includes a first planetary gear unit U0, a multi-plate clutch C0 operated by a hydraulic servo, and a multi-plate brake.
An overdrive transmission 300A including B0 and a one-way clutch F0, a second planetary gear device U1, a third planetary gear device U2 to which the present invention is applied, two multi-plate clutches C1 and C2 operated by hydraulic servos, It is composed of a belt brake B1, two multi-plate brakes B2 and B3, and an underdrive transmission 300B having three forward gears and one reverse gear provided with two one-way clutches F1 and F2.

The transmission case 110 of the automatic transmission 100 is a torque converter.
A torque converter housing 120 that accommodates 200, a transmission case 130 that integrally forms each chamber that accommodates an overdrive transmission 300A and an underdrive transmission 300B, and an extension housing 140 that covers the rear side of the automatic transmission 100. Which are fastened together with a large number of bolts.

The torque converter 200 is housed in a torque converter housing 120 whose front side (engine side) is open, and is rotated by the drive of an engine (not shown).
1, an annular rear cover 202 welded to the inner periphery thereof, a pump impeller 203 provided on the inner peripheral wall of the rear cover 202, and a turbine runner 2 arranged to face the pump impeller 203
A turbine shell 205 holding 04, a stator 208 supported by a fixed shaft 207 connected to a transmission case 110 via a one-way clutch to increase torque capacity when the input speed is low, a front cover 201 and a turbine shell 205. A direct coupling clutch (lock-up clutch) 209 is provided between the two and directly couples them.

The external gear 150a and the internal gear 1 are internally provided between the tubular transmission case 130 and the torque converter housing 120, which are continuous to the rear of the torque converter housing 120.
An internal gear oil pump 150 including 50b is accommodated, and an oil pump body 152 having a tubular portion 151 protruding forward on the inner periphery is fastened to the front portion of the transmission case 130, and an inner peripheral end portion of the rear cover 202. Connected extension member 210
Is spline-fitted to the inner circumference of the external gear 150a through the inner circumference of the tubular portion 151. Also, the oil pump body 152
On the rear side, an oil pump cover 1 having a tubular front support 153 coaxial with the tubular portion 151 and projecting rearward
The oil pump housing 152 and the oil pump cover 154 form a partition wall between the torque converter housing 120 and the transmission case 130 when the oil pump housing 152 and the oil pump cover 154 are fastened.

Further, in the middle of the transmission case 130, a wall that separates the overdrive mechanism chamber 130A in which the overdrive transmission 300A is arranged and the underdrive mechanism chamber 130B in which the underdrive transmission 300B is arranged is formed. Further, a center support 132 having a cylindrical support portion 131 protruding rearward is provided.

A rear support wall 134 having a cylindrical rear support 133 protruding forward is provided at a rear portion (right side in the drawing) of the transmission case 130.

Inside the front support 153, the torque converter 200
Fixed shaft 20 of one-way clutch 206 supporting stator 208 of
7, the input shaft 10 of the transmission 300, which is the output shaft of the torque converter 200, is rotatably supported inside. At the rear end of the input shaft 10, the flange 10
1 is provided, and a rearward facing hole 102 is formed in the center thereof. Behind the input shaft 10, an intermediate transmission shaft 11 arranged in series with the input shaft 10 is rotatably mounted.
11, the tip is inserted into the hole 102 of the input shaft 10, has a flange portion 11 at the rear end, the rear end of the output shaft 12 for transmitting power to the drive wheel side in the center is inserted backward. The hole 112 is provided. The output housing 12 has an extension housing 140
A sensor rotor 121 for detecting the number of revolutions and a speedometer drive gear 122 are fixed inside, and a spline groove 123 is formed on the outer periphery at the rear end for inserting a sleeve yoke for transmitting power to the drive wheels. The output shaft 12 is rotatably supported by the extension housing 140 via the sleeve yoke, and its front side is rotatably supported by the hole 112 of the intermediate transmission shaft 11 and the inner circumference of the rear support 133. There is.

The overdrive transmission 300A has a first rear side of the input shaft 10.
Equipped with a planetary gear unit U0, the ring gear R0 of which is an intermediate transmission shaft.
The planetary carrier P0 is connected to the flange portion 101 of the input shaft 10, and the sun gear S0 is formed by the inner race shaft 13 of the one-way clutch F0. On the front side of the first planetary gear unit U0, a first hydraulic servo drum 14 that opens rearward is fixedly disposed on the inner race shaft 13, and an outer peripheral wall 14A of the first hydraulic servo drum 14 is provided.
The annular piston 15 is fitted between the inner peripheral wall 14B and the inner peripheral wall 14B to form the hydraulic servo C-0 of the clutch C0 which engages and disengages the carrier P0 and the first hydraulic servo drum 14, and
An annular piston 15 is attached to the inner race shaft 13 by a hydraulic servo C-
A clutch C0 is mounted inside the return spring 16 and the outer peripheral wall 14A that are pressed toward the 0 side, and the first clutch
Hydraulic servo drum 14, inner race shaft 13 and carrier P0
And are connected. A one-way clutch F0 having an inner race shaft 13 as an inner race is provided on the inner circumference of the first hydraulic servo drum 14, and a clutch C0 and a brake B are provided on the outer circumference between the outer race 17 and the transmission case 130.
0 is provided, a piston 18 for pressing the brake B0 is fitted in front of the center support 132 behind the brake B0, and the brake B is interposed between the piston 18 and the center support 132.
A hydraulic servo B-0 of 0 is formed, and the piston 18 is mounted on the front end inner peripheral portion 135 of the center support 132.
A return spring 19 that presses to the side is fitted.

In the underdrive transmission 300B, the second hydraulic servo drum 20 that opens to the rear is first provided in the center support 13 at the front.
An annular piston 21 for pressing the clutch C2 is fitted between the outer peripheral wall 20A and the inner peripheral wall 20B of the second support portion 131 so as to be rotatably inserted therein. A hydraulic servo C-2 of the clutch C2 is formed between the hydraulic servo drums 20, a return spring 22 for pressing the annular piston 21 toward the hydraulic servo C-2 side is attached to the inner peripheral wall 20B side, and an outer peripheral wall 20A side. Clutch C2 is installed inside. Behind the second hydraulic servo drum 20, there is provided a third hydraulic servo drum 24 having a rearward opening and an annular projection 23 at the front thereof, which is a flange portion 11 at a rear portion of the intermediate transmission shaft 11.
The rear end of the intermediate transmission shaft 11, the outer peripheral wall 24A of the third hydraulic servo drum 24, and the flange portion 111 are fixedly provided on the outer periphery of the first hydraulic servo drum.
A ring-shaped piston 25 for pressing the clutch C1 is fitted between the ring-shaped piston 25 and the third hydraulic servo drum.
A hydraulic servo C-1 of the clutch C1 is formed between 24, and a return spring 26 for pressing the annular piston 25 toward the hydraulic servo C-1 side is mounted on the inner peripheral side of the clutch C1. Clutch C2 is attached to the outer periphery,
The second and third hydraulic servo drums 20 and 24 are connected via the clutch C2.

FIG. 1 is an enlarged sectional view showing a portion to which the forced lubrication mechanism of the present invention is applied. Behind the third hydraulic servo drum 24, a sun gear shaft 29 rotatably fitted around the outer periphery of the output shaft 12. 1 integrally provided at the front end of the sun gear 1, a pinion gear 2 that meshes with the sun gear 1, a ring gear 3 that meshes with the pinion gear 2 on the outer periphery of the pinion gear 2, and a pinion gear 2
A pinion shaft 4A that rotatably supports via a bearing roller 2A held by a case 2B, and both axial end surfaces of the pinion gear 2 via a thrust washer 2C, and the inner circumference is splined to the output shaft 12. Shaft support part that is fitted and installed to support the pinion shaft 4A
A second planetary gear unit U1 consisting of a pinion carrier 4 with 4B is provided. Ring gear 3 outputs it
It is connected to the third hydraulic servo drum 24 via an annular protrusion 28 and a clutch C1 which are provided in front of a rotation support member 27 which is rotatably supported on the outer periphery of 12. The pinion carrier 4 includes a shaft support portion 4B of the pinion shaft 4A.
From the axial end surface 4C on the side of the pinion shaft 4A to the central portion of the outer periphery 4D of the pinion shaft 4A, and an oil passage 4E in the shaft that passes through the inside of the pinion shaft 4A is formed. A cutting groove 4H is formed. Shaft support
An oil reservoir 4E is provided on the front end surface of 4B, with the outer circumference being locked to the end surface of the shaft support portion 4B in a state where the inner circumference side is open so as to store the lubricating oil in the oil 4G. FIGS. 3 and 4 show the shape of the oil reservoir 4F. As shown in these figures, the oil reservoir 4F is made of a press-molded product and is formed into an annular shape so that it is brought into contact with the end surface of the pinion shaft 4A. And is fixed to the carrier 4. Therefore, the oil reservoir 4F is provided with claws 4J for caulking the outer periphery of the carrier 4 at four locations on its outer periphery,
Also, the pinion shaft 4A can be attached to the carrier 4
Bulging portions 4L are formed at four places of the intermediate diameter portion facing the end surface to form an oil inflow path between the bulging portion 4L and the end surface.
A guide portion 4K bent in a direction away from the end face of the pinion shaft 4A is formed in the inner periphery so as to form an opening for taking in oil with the end face of the pinion shaft 4A.

A thrust bearing 5 is interposed between the shaft support portion 4B and the rotation support member 27 so that they can rotate relative to each other, and a thrust trace 5A on the front side thereof contacts the rotation support member 27, The rear side thrust race 5B is in contact with the shaft support portion 4B. The flange portion 5C on the outer peripheral side of the thrust trace 5A is formed with a bent portion which is bent in the axial direction toward the shaft support portion 4B so as to overlap the bent guide portion 4K of the oil reservoir 4F in the axial direction. A gap A narrower than the opening of the oil reservoir 4F is provided between the tip of the portion 5C and the end surface of the shaft support portion 4B.

The opening of the oil reservoir 4F opens between the front surface of the shaft support portion 4B and the rear surface of the rotation support portion 27, and extends from the in-shaft lubricating oil supply oil passage 12A in the output shaft 12 to the shaft support portion 4B and the rotation support portion. The rotary support 27 faces the thrust trace of the bearing 5 and faces the outer peripheral discharge oil passage 6A for supplying lubricating oil between the two.
It is provided with a protruding portion 27A protruding rearward so as to support 5A on the outer peripheral side.

The lubrication oil is supplied to the forced lubrication mechanism as follows. That is, the engine is driven to drive the oil pump 150 via the rear cover 202 of the torque converter 200, and the lubricating oil is supplied into the in-shaft lubricating oil supply passage 12A. Then, when the output shaft 12 receives power transmission, the lubricating oil in the in-shaft lubricating oil supply passage 12A is discharged from the outer peripheral discharge oil passage 6A between the shaft support portion 4B and the rotation support portion 27 by centrifugal force or hydraulic pressure. The discharged oil lubricates the bearing 5 arranged between the shaft support portion 4B and the rotor time portion 27, is squeezed by the gap A, flows out to the outer peripheral side, and is collected in the opening of the oil reservoir 4F. . The oil collected in the oil reservoir 4F is supplied into the shaft oil passage 4E and flows out between the pinion gear 2 and the pinion shaft 4A through the opening at the center of the outer circumference 4D. The oil that has flowed out between the pinion gear 2 and the pinion shaft 4A forcibly lubricates the bearing roller 2A, the cage 2B, and the thrust washer 2C.

Returning to FIG. 2, the connecting drum 30 molded so as to cover the second and third hydraulic servo drums 20, 24 and the second planetary gear unit U1 in the minimum space has the front end thereof at the second hydraulic servo drum 20. Fixed to the outer periphery of the second end of the second planetary gear unit U1
Is connected to the sun gear shaft 29 at the rear of the
On the outer peripheral side of the belt brake to fix and release
B1 is provided.

The spline 136 formed on the inner periphery of the rear part of the transmission case 130 is spline-fitted with the brake plate b2 of the brake B2 on the front side and the brake plate b3 of the brake B3 on the rear side, and between the brake B2 and the brake B3. A fourth hydraulic servo drum 32, which is open to the front and has an annular projection 31 on the front side, is spline-fitted and attached. Outer peripheral wall 32A of fourth hydraulic servo drum 32 and annular projection 3
An annular piston 33 that presses the brake B2 is fitted between 1 to form a hydraulic servo B-2 of the brake B2 between the annular piston 33 and the fourth hydraulic servo drum 32, and an annular piston is provided on the inner peripheral wall 32B side. A return spring 34 for pressing the piston 33 is provided. A one-way clutch F1 having a sun gear shaft 29 as an inner race is provided on the inner circumference side of the brake B2, and a brake is provided on the outer circumference of the outer race 35.
B2 is installed. Rear support wall behind brake B2 134
Rear support 133 Outer side and transmission case 1
A plurality of pistons 371, 373 for pressing the brake B3 and a reaction sleeve 372 are fitted in the annular hole 36 formed between the 30 to form a hydraulic servo B-3 of the brake B3. The return spring 38 that presses to the hydraulic servo B-3 side has a rear support 133.
It is supported by a return spring fitting 38A attached to the tip. The inner race 39 of the one-way clutch F2 arranged on the inner circumference of the brake B3 is connected to the fourth servo drum 32 on the outer circumference of the sun gear shaft 29, and the brake B3 is mounted on the outer circumference of the outer race 40 of the one-way clutch F2. ing.

In the third planetary gear train U2, the sun gear S2 has a sun gear shaft 29.
One-way clutch with carrier P2 formed integrally with
Brake B3 coupled with the outer race 40 of F2
A ring gear R2, which is connected to the output shaft 12 and has a parking gear 41 formed on the outer circumference, is connected to the output shaft 12 via a connecting member 42 that is spline-fitted to the output shaft 12. The parking gear 41 parks the shift lever of the automatic transmission (P).
When the position is selected, the parking claw 43 is provided so as to mesh with and fix the output shaft 12.

Transmission 300 of this embodiment configured as described above, by the hydraulic pressure selectively output to the hydraulic servo of each friction engagement device from the hydraulic control device 400 according to the vehicle traveling conditions such as vehicle speed and throttle opening, By engaging or disengaging the respective clutches and brakes, four forward gear shifts and one reverse gear shift are performed. The hydraulic control device 400
Is provided in a valve body 403 incorporated in an oil pan 402 that is fastened to the lower portion of the transmission case 130 by a bolt 401. Table 1 shows an example of the operation of each clutch, brake, and one-way clutch and the achieved shift speed (RANGE).

In Table 1, E indicates that the corresponding clutch and brake are engaged, and X indicates that they are released. L has a corresponding one-way clutch engaged in the engine drive state, but the engagement is not always required because the transmission of power is ensured by a clutch or a brake installed in parallel with the one-way clutch ( Lock). (L) indicates that the corresponding one-way clutch is engaged only in the engine drive state and is not engaged in the engine brake state. Further, f indicates that the corresponding one-way clutch is free.

As described above in detail, according to the apparatus of this embodiment, the oil discharged from the outer peripheral discharge oil passage 6A of the speed change shaft 12 and lubricating the bearing 5 is deflected and guided by the flange 5C of the thrust race and is effective in the oil reservoir 4F. Therefore, a sufficient amount of lubricating oil is supplied to the oil port 4G of the oil passage 4E in the shaft,
An effective forced lubrication effect can be obtained.

The present invention has been described above based on the embodiment, but the present invention is not limited to the above-mentioned embodiment, and various detailed configurations may be changed within the scope of the matters described in the claims. It goes without saying that it is feasible.

[Brief description of drawings]

FIG. 1 is a sectional view showing a main part of an automatic transmission to which a forced lubrication device according to an embodiment of the present invention is applied, FIG. 2 is a sectional view showing the whole thereof, and FIG. 3 is a front view of an oil reservoir thereof. 4 is a sectional view taken along the line AA of FIG. 1 ... Sun gear, 2 ... Pinion gear, 2A ... Bearing, 3 ... Ring gear, 4 ... Carrier, 4A ... Pinion shaft, 4B ... Shaft support, 4E ... Oil passage in shaft, 4F ... … Oil reservoir, 4K …… Guide part, 5 ……
Thrust bearing, 5A, 5B ... Thrust trace, 5C ...
… Flange (bent part), 6A …… Outer peripheral discharge oil passage, 11 …… Intermediate transmission shaft, 12 …… Output shaft

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Toyohata, Toyota City, Aichi Prefecture, 1 Toyota Town, Toyota Motor Co., Ltd. (72) Inventor, Kazuaki Watanabe, Toyota City, Aichi Prefecture 1, Toyota Town, Toyota Motor Co., Ltd.

Claims (1)

[Claims] 1. A planetary gear device which is disposed on a shaft and has a ring gear, a pinion gear, a sun gear, a pinion shaft that rotatably supports the pinion gear via bearings, and a carrier that supports the pinion shaft, and the shaft. An outer peripheral discharge oil passage formed in the shaft, an in-shaft oil passage formed from the axial end of the pinion shaft toward the inside of the shaft to guide lubricating oil from the outer peripheral discharge oil passage to the bearing, and an oil in the shaft. In a forced lubrication device of a planetary gear device including an oil reservoir provided at an axial end of the pinion shaft to guide lubricating oil to a passage, an inner circumference of the oil reservoir is bent in a direction away from the axial end of the pinion shaft. A guide portion is formed, and the guide is formed on the inner side of the oil reservoir and on the outer side of the outer peripheral discharge oil passage in the radial direction. A thrust bearing that restricts the axial movement of the gear device is disposed, and a bent portion that bends in the axial direction toward the pinion shaft support portion side is formed on the outer periphery of the thrust trace of the thrust bearing, and the guide portion and the bent portion are A forced lubrication device for a planetary gear device, which is characterized by overlapping in the axial direction.