JPS6138249A - Forced lubricating mechanism of planetary gear device - Google Patents

Abstract

PURPOSE:To reliably lubricate a portion between a pinion gear and a pinion carrier by forming an intra-shaft oil passage on a pinion shaft and fitting an oil reservoir on the side face of a shaft support section via an oil seal material. CONSTITUTION:An intra-shaft passage 4E communicating the axial side face 4C of a shaft support section 4B side and the outer periphery face 4D of the pinion shaft 4A is formed on the pinion shaft 4A, and an oil reservoir 4F supplying lubricating oil to the oil port of the intra-shaft passage 4E is fitted to the side face of the shaft support section 4B. Accordingly, the lubricating oil fed to the oil reservoir 4F is fed to the intra-shaft passage 4E without being leaked to the outside due to the oil seal member 5, thus a portion between a pinion gear 2 and a pinion carrier 4 can be reliably lubricated.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a forced lubrication mechanism for a planetary gear set provided in an automatic transmission.

[Prior Art] Conventionally, in an automatic transmission, a 1M star gear device consisting of a sun gear, a pinion gear, a pinion carrier, and a ring gear performs deceleration, speed increase, direct connection, etc. of input rotation by switching the input direction and output direction. When the vehicle is running, the pinion is constantly driven to rotate, and in particular, the pinion is frequently rotated at high speeds because power is transmitted through the pinion unless the pinion is in a directly connected state. For this purpose, a roll bearing or the like is arranged on the inner periphery of the pinion and fitted onto the pinion shaft, and a thrust washer is arranged between the axial side surface and the shaft support part, and a sun gear on the inner periphery of the pinion and a center An oil passage is provided to discharge lubricating oil from the side shaft to the thrust washer to improve the durability of the binion.

[Problems to be solved by the invention] In the conventional technology shown above, only the thrust washer is forced to lubricate, and the bearing placed between the pinion gear and the pinion shaft is lubricated by the lubricating oil supplied to the thrust washer. As a result, the bearings were not sufficiently lubricated, and there was a risk that the pinion shaft and pinion gear would not have sufficient durability. Therefore, in order to solve the above problem, the pinion carrier has an in-shaft oil passage that communicates the axial side surface of the pinion shaft on the shaft support part side and the outer circumferential surface of the pinion shaft, and is attached to the side surface of the shaft support part. A method has been proposed for forcibly lubricating the space between the pinion gear and the pinion shaft by providing an oil reservoir that supplies lubricating oil to the cuff of the in-shaft oil passage that opens on the axial side surface of the shaft support part. If there is a gap between the contact surface between the oil reservoir and the shaft support, lubricating oil cannot be stored in the oil reservoir, so the flatness of the shaft support to which the oil reservoir is attached and the accuracy of the contact surface of the shaft support of the oil reservoir However, even if the contact surface of the shaft support to which the oil reservoir is attached and the contact surface of the shaft support of the oil reservoir are maintained at a high level of accuracy, production costs will increase. Due to the above variations, there was a concern that a gap would occur at the contact surface between the oil reservoir and the shaft support.

An object of the present invention is to provide an in-shaft oil passage that communicates the axial side surface of the pinion shaft on the shaft support side and the outer circumferential surface of the pinion shaft with a pinion carrier of a planetary gear device;
An oil reservoir is provided that is attached to the side surface of the shaft support portion and supplies lubricating oil to the cuff of the in-shaft oil passage that opens on the side surface in the axial direction on the shaft support portion side, and the oil reservoir is provided between the side surface of the shaft support portion and the cuff of the shaft oil passage. To provide a forced lubrication mechanism for a planetary gear device, which improves lubrication between a pinion gear and a pinion shaft and improves oil sealing properties at a contact surface between an oil reservoir and a shaft support part by being attached to the pinion gear via an oil seal material.

[Means for solving the problem] Strong control of the planetary gear device of the present invention 1! In order to solve the above problem, the sliding mechanism includes a 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, and a pinion shaft that rotatably fits the pinion gear 2. 4A and a pinion carrier 4 consisting of a shaft support part 4B that supports the pinion shaft 4A, the pinion carrier 4 supports the shaft support part 4 of the pinion shaft 4A.
An in-shaft oil passage 4E that communicates the axial side surface 4C on the B side with the outer circumferential surface 4D of the pinion shaft 4A, and an axial oil passage 4E that is attached to one side surface of the shaft support section 4B and communicates with the axial direction side surface 4C on the B side and the outer peripheral surface 4D of the pinion shaft 4A. An oil reservoir 4F for supplying lubricating oil is provided at the cuff of the in-shaft oil passage 4E that opens on the side surface 4C, and the oil reservoir 4F is attached via an oil seal material 5 between the side surface of the shaft support portion 4B. The composition consists of the following.

[Function] The forced lubrication mechanism of the planetary gear device of the present invention having the above-mentioned configuration has the lI! of the inner circumference of the oil reservoir 5. ! The lubricating oil discharged from the lubricating oil supply means is stored in the oil reservoir 4F by centrifugal force, and the stored lubricating oil flows through the in-shaft oil passage 4E that opens to the axial side surface 4C on the shaft support portion 4B side. The oil is supplied from the oil port to the outer circumferential surface 4D of the pinion shaft 4A, and forcibly lubricates between the pinion gear 2 and the pinion shaft 4A, and between the pinion gear 2 and the shaft support portion 4B.

[Effects of the Invention] The forced lubrication mechanism for a planetary gear device of the present invention having the above configuration has the following effects.

b) An in-shaft oil passage that communicates between the axial side surface of the shaft support part of the binion shaft and the outer circumferential surface of the pinion shaft, and An oil reservoir for supplying lubricating oil is provided at the cuff of the oil passage in the shaft to be opened, and the oil reservoir is installed between the side surface of the shaft support part via an oil seal material, so that the oil is supplied to the oil reservoir. The lubricating oil is supplied to the oil passage inside the shaft by the oil seal material without leaking to the outside, and reliably lubricates between the pinion gear and the pinion carrier.

(portion) The oil seal material is interposed between the contact surface of the shaft support portion of the oil reservoir and the side surface of the shaft support portion to which the oil reservoir is attached. Since there is no need to maintain high precision on the contact surface, production costs can be reduced.

c) Since the oil seal material is interposed between the contact surface of the shaft support part of the oil reservoir and the side surface of the shaft support part, the oil reservoir can be easily assembled even if the assembly precision is low when assembling the oil reservoir to the shaft support part. Since airtightness can be maintained between the shaft support portion and the shaft support portion, ease of assembly is improved.

[Embodiment] Next, a forced lubrication mechanism for a planetary gear apparatus according to the present invention will be described based on an embodiment shown in the drawings.

FIG. 1 is a cross-sectional view showing a forced lubrication mechanism for a planetary gear apparatus according to the present invention, and FIG. 2 is a cross-sectional view of an automatic transmission for a vehicle to which the forced lubrication mechanism for a planetary gear apparatus according to the present invention is applied.

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 device UO1
One multi-disc clutch C01 operated by hydraulic servo
An overdrive transmission 300A including one multi-disc brake BO1 and one one-way latch FO, a second planetary gear unit U1, a third planetary gear unit U2, to which the present invention is applied. Two multi-disc clutches C1, C2, one belt brake B1, two multi-disc brakes B2, B3 and two one-way latches F operated by hydraulic servos.
1, an underdrive transmission @ 300B with 3 forward speeds and 1 reverse speed equipped with F2.

The transmission case 110 of the automatic transmission@ioo is a transmission case 130 that is integrally formed with a torque converter housing 120 that houses a torque converter 200, and chambers that house an overdrive transmission 300A and an underdrive transmission 300B. , and an extension housing 140 that covers the rear side of the automatic transmission 100, and the torque converter housing 120, transmission case 130, and extension housing 140 are each fastened with a large number of bolts.

The torque converter 200 is housed in a torque converter housing 120 that is open at the front (engine side), and includes a front cover 201 that rotates under the drive of an engine (not shown), and an annular plate welded to the inner circumference of the front cover 201. A rear cover 202 having a shape, a pump impeller 203 disposed around the inner peripheral wall of the rear cover 202, a turbine runner 204 disposed opposite to the pump impeller 203, and a turbine shell 205 holding the turbine runner 204. , the stator 20 is supported by a fixed shaft 207 connected to the transmission case 110 via a one-way clutch 206, and increases the torque capacity when the input rotation speed is low.
8. The front cover 201 and the turbine shell 205
between the front cover 201 and the turbine shell 205
A direct coupling clutch (lock-up clutch) 209 is provided that rotates the same rotation. An internal gear oil pump 150 having an external gear 150a and an internal gear 150b is housed between the cylindrical transmission case 130 and the torque converter housing 120, which are continuous to the rear of the torque converter housing 120. Oil pump body 15 having a cylindrical portion 151 protruding forward on the inner periphery
2 is fastened to the front part of the transmission case 130, and the extension member 2 is connected to the inner peripheral end of the rear cover 202.
10 is spline-fitted to the inner circumference of the external gear 150a via the inner circumference of the cylindrical portion 151. Further, an oil pump cover 154 having a cylindrical front support 153 that is coaxial with the cylindrical portion 151 and protrudes rearward is fastened to the rear side of the oil pump body 152 to connect the oil pump housing 152 and the oil pump. Cover 154 forms a partition between torque converter housing 120 and transmission case 130. Further, in the middle of the transmission case 130, there is a cylindrical wall projecting rearward that partitions an overdrive mechanism chamber 130A in which an overdrive transmission 300A is formed and an underdrive mechanism chamber 130B in which an underdrive transmission 300B is formed. A center support 132 having a support portion 131 is provided. A rear support wall 134 having a cylindrical support support 133 projecting forward is provided at the rear (right side in the figure) of the transmission case 130.

Inside the front support 153 is a one-way clutch 2 that supports the stator 208 of the torque converter 200.
06 fixed shaft 207 is fitted, and the input shaft 10 of the transmission 300, which is the output shaft of the torque converter 200, is rotatably supported inside the fixed shaft 207. The input shaft 10 has a flange portion 101 at the rear end,
A rearward facing hole 102 is formed in the center of the rear end.

An intermediate power transmission shaft 11 arranged in series with the input shaft 10 is rotatably mounted behind the input shaft 10, and the tip of the intermediate power transmission shaft 11 slides into a hole 102 of the input shaft 10. , a clutch portion 111 is provided at the rear end of the intermediate transmission shaft 11, and a rearward-facing hole 112 is formed in the center of which the tip of an output shaft 12 that transmits power to the driving wheels slides. Output shaft 1
2 fixes the sensor rotor 121 for rotation speed detection and the speedometer drive gear 122 in the extension housing 140, and the rear end has a spline groove 12 on the outer periphery to fit the sleeve yoke that transmits power to the drive wheel side.
3 is formed, and is rotatably supported by the extension housing 140 via the sleeve yoke, and the front end is rotatably supported within the hole 112 of the intermediate transmission shaft 11 and the inner periphery of the rear support 133.

The overdrive transmission 300A has the input shaft 10
A first planetary gear unit UO is provided behind the , the ring gear RO is coupled to the intermediate transmission shaft 11 via a flange plate 113, the planetary carrier PO is coupled to the clutch portion 101 of the input shaft 10, and the Zangia SO is It is formed by the inner race shaft 13 of the one-way latch FO.

First planetary gear device tJ.

On the front side, there is a first hydraulic servo drum 14 that opens rearward.
is fixed to the inner race shaft 13, and an annular piston 15 is fitted between the outer circumferential wall 14A and the inner circumferential wall 14B of the first hydraulic servo drum 14 to engage and disengage the fourth near rear PO and the first hydraulic servo drum 14. It forms the hydraulic servo C-0 of the clutch CO and also the inner race shaft 13.
A return spring 16 that presses the annular piston 15 toward the hydraulic servo C-θ side is installed on the side, and a clutch CO is installed inside the outer peripheral wall 14A, and the first hydraulic servo drum 14 and inner race shaft 13 are connected to the carrier via the clutch CO. It is connected to PO. A one-way latch FO with the inner race shaft 13 as an inner race is provided on the inner periphery of the first hydraulic servo drum 14, a clutch GO and a brake BO are provided on the outer periphery between the outer race 17 and the transmission case 130, and a brake A piston 18 that presses the brake BO is fitted in front of the center support 132 at the rear of the BO, and between the piston 18 and the center support 132 is the hydraulic servo B of the brake BO.
-0, and a return spring 19 that presses the piston 18 toward the hydraulic servo B-0 is fitted into the inner peripheral portion 135 of the front end of the center support 132.

In the underdrive transmission 300B, first, a second hydraulic servo drum 20 that opens rearward is rotatably fitted around the outer periphery of the support portion 131 of the center support 132, and a second hydraulic servo drum 20 that opens rearward is rotatably fitted between the outer circumferential wall 20A and the inner circumferential wall 20B. clutch C2
An annular piston 21 that presses the clutch C2 is fitted between the annular piston 21 and the second hydraulic servo drum 20.
A return spring 22 that forms the hydraulic servo C-2 and presses the annular piston 21 toward the hydraulic servo C-2 on the inner peripheral wall 20B side, and a clutch C on the inside of the outer peripheral wall 20A.
2 is installed. At the rear of the second hydraulic servo drum 20, a third hydraulic servo drum 24 which is open toward the rear and has an annular projection 23 at the front is fixed to the outer periphery of the flange portion 111 at the rear portion of the intermediate transmission shaft 11. An annular piston 25 that presses the clutch C1 is fitted between the rear end of the intermediate transmission shaft 11, the outer peripheral wall 24A of the third hydraulic servo drum 24, and the outer periphery of the flange portion 111, and the annular piston 25 and the third hydraulic pressure are connected to each other. Hydraulic servo C of clutch C1 between servo drum 24
-1, an annular piston 25 on the inner circumference side of the clutch C1, a return spring 26 that presses the hydraulic servo C-1 side, and a clutch C2 on the outer circumference of the annular protrusion 23.
is attached, and the second and third hydraulic servo drums 20 and 24 are connected via a clutch C2. Behind the third hydraulic servo drum 24, a sun gear 1 is provided integrally with the front end of a sun gear shaft 29 that is rotatably fitted around the output shaft 12, and a pinion gear 2 that meshes with the sun gear 1. , a ring gear 3 meshing with the pinion gear 2 on the outer periphery of the pinion gear 2, a roll bearing 2A from the inner periphery of the pinion gear 2, and a gauge 2B disposed between the roll bearings 28 and maintaining the position of the roll bearing 2A. The pinion shaft 4A is rotatably supported through the pinion shaft 4A, and the pinion shaft 4A is supported through the thrust washer 2C between the pinion shaft 4A and the axial side surface of the pinion gear 2. A second planetary gear device U1 is provided which includes a pinion carrier 4 including a shaft support portion 4B, and a ring gear 3 is located in front of a rotation support member 27 that rotatably supports the ring gear 3 on the outer periphery of the output shaft 12. The pinion carrier 4 is connected to the third hydraulic servo drum 24 via an annular protrusion 28 and a clutch C1 provided in a protruding manner. An inner shaft oil passage 4E whose outer circumference 4D communicates with the inside of the pinion shaft 4A, a cutting groove 4H1 formed on the inner circumference side from the cuff 4G of the axial side surface 4C of the shaft inner passage 4E, and a cutting groove 4H1 on the front side of the shaft support portion 4B. An oil reservoir 4F, which is attached to the side surface and whose outer periphery is a press-molded product formed as shown in FIGS. 3 and 4, is provided on the side surface of the shaft support portion 4B so as to store lubricating oil in the cuff 4G. As shown in FIG. 5, between the oil reservoir 4F and the side surface of the shaft support part 4B, there is a rubber fitting that corresponds to the contact shape between the oil reservoir 4F and the shaft support part 4B so that the oil reservoir 4F does not leak lubricating oil to the outer periphery. An oil seal material 5 made of cork, cork, or the like is provided. The opening of the oil reservoir 4F is opened between the front surface of the shaft support section 4B and the rear surface of the rotation support section 27,
On the inner periphery between the shaft support part 4B and the rotation support part 27, which is the inner periphery of the oil reservoir 4F, there is an in-shaft lubricating oil supply oil passage 12A in the output shaft 12 between the shaft support part 4B and the rotation support part 27. An outer peripheral discharge oil passage 6A is provided for supplying lubricating oil to the rotary support part 27, and a protrusion part 27A that protrudes rearward is provided at the inner peripheral position of the opening of the oil reservoir 4F to narrow the space between the rotary support part 27 and the shaft support part 4B. The lubricating oil supplied between the shaft support part 4B and the rotation support part 27 is forcibly supplied to the oil reservoir 4F. In the above operation, when the engine is driven, the oil pump is driven through the rear cover 202 of the torque converter 200, and lubricating oil is supplied into the shaft lubricating oil supply path 12A. When the output shaft 12 receives power transmission, the lubricating oil in the intrashaft Il lubricating oil supply path 12A is discharged between the shaft support portion 4B and the fixed support portion 270 from the outer peripheral discharge oil path 6A by centrifugal force or hydraulic pressure. The discharged lubricating oil passes through the roll bearing 27D having a bearing race 27B127G arranged between the shaft support part 4B and the rotation support part 27, and then through the gap between the protrusion part 27A and the shaft support part 4B. It is supplied into the opening of the reservoir 4F. The lubricating oil supplied into the oil reservoir 4F is supplied into the shaft inner oil passage 4E without leaking to the outer circumference by the oil seal material 5, and flows out between the pinion gear 2 and the pinion shaft 4A through the opening on the outer circumference 4D. . The lubricating oil spilled between the pinion gear 2 and the pinion shaft 4A forcibly lubricates the roll bearing 2A, gauge 2B, and thrust washer 2C. Also, the second
．． A connecting drum 30 molded to cover the three hydraulic servo drums 20, 24 and the second planetary gear unit U1 with a minimum space is fixed at its front end to the outer periphery of the second hydraulic servo drum 20, and its rear end is fixed to the outer periphery of the second hydraulic servo drum 20. 2 Connected to the sun gear shaft 29 at the rear of the planetary gear system 1, and a connecting drum 30 on the outer peripheral side.
A belt brake B1 is provided for fixing and releasing.

A brake plate b2 of the brake B2 at the front and a brake plate b3 of the brake B3 at the rear are spline-fitted to a spline 136 formed on the inner periphery of the rear part of the transmission case 130. and an annular projection 31 on the front side.
A fourth hydraulic servo drum 32 is spline-fitted. An annular piston 33 that presses the brake B2 is fitted between the outer peripheral wall 32^ of the fourth hydraulic servo drum 32 and the annular projection 31, and a hydraulic servo 3- of the brake B2 is fitted between the annular piston 33 and the fourth hydraulic servo drum 32. 2
At the same time, an annular piston 33 is formed on the inner peripheral wall 32B side.
return spring 3 that presses the hydraulic servo 3-2 side
4 is provided. Also, on the inner peripheral side of the brake B2, there is a one-way latch F that uses the sun gear shaft 29 as an inner race.
1 is provided, and a brake B is provided on the outer periphery of the outer race 35.
2 is installed. Rear support wall 1 on the rear side of brake B2
The brake B is inserted into the annular hole 36 formed between the outer circumferential side of the rear support 133 of 34 and the transmission case 130.
A plurality of pistons 371, 373 and reaction sleeve 372 are fitted to form hydraulic servo B-3 of brake B3, and return spring 38 presses pistons 371 and 313 toward hydraulic servo B-3.
is supported by a return spring attachment 38A attached to the tip of the rear support 133. Brake B3
The inner race 39 of the one-way latch F2 arranged on the inner periphery of the fourth hydraulic servo drum 3 is on the outer periphery of the sun gear shaft 29.
2 and the outer race 4 of the one-way clutch F2
Brake B3 is attached to the outer circumference of 0. In the third planetary gear device u2, a sun gear S2 is formed integrally with a sun gear shaft 29, a carrier P2 is connected to an outer race 40 of a one-way clutch F2 on the front side, and a brake B3, and a parking gear 41 is arranged around the outer periphery. The provided ring gear R2 is connected to the output shaft 12 via a connecting member 42 whose inner circumference is spline-fitted. The parking gear 4
1, when the shift lever of the automatic transmission is selected to the parking (P) position, the parking pawl 43 moves to the parking gear 4.
1 to fix the output shaft 12.

The transmission 300 changes the transmission case 1 according to vehicle driving conditions such as vehicle speed and throttle opening.
Each clutch and brake is controlled by hydraulic pressure selectively output to the hydraulic servo of each llj friction engagement device from a hydraulic control device 400 in a valve body 403 built in an oil pan 402 fastened to the lower part of the 30 with a bolt 401. The engagement or disengagement is performed to perform four forward speeds or one reverse speed change. The operation of each clutch, brake, and one-way clutch and the gear stage CRANG achieved
Examples of E) are shown in Table 1.

Table 1 In Table 1, E indicates that the corresponding clutch or brake is engaged, and × indicates that the corresponding clutch or brake is disengaged.

Although the corresponding one-way clutch is engaged in the engine drive state, this engagement is not necessarily required since power transmission is guaranteed by a clutch or brake built in parallel with it ( 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. Roughly f indicates that the corresponding one-way clutch is free.

[Brief explanation of the drawing]

FIG. 1 is a side cross-sectional view showing a forced lubrication mechanism for a planetary gear apparatus according to the present invention, FIG. 2 is a side cross-sectional view of an automatic transmission for a vehicle to which the forced lubrication mechanism for a planetary gear apparatus according to the present invention is applied, and FIG. is a front view of the oil reservoir, and Figure 4 is the A-A shown in Figure 3.
A sectional view taken along a line, FIG. 5 shows a front view of the oil seal.

Claims (1)

[Scope of Claims] 1) A sun gear, a pinion gear that meshes with the sun gear, a ring gear that meshes with the pinion gear, a pinion shaft that rotatably fits the pinion gear, and a shaft that supports the pinion shaft. In a planetary gear device comprising a pinion carrier comprising a support part, the pinion carrier has an in-shaft oil passage communicating between one axial side surface of the shaft support part of the pinion shaft and an outer circumferential surface of the pinion shaft. , an oil reservoir that is attached to one side surface of the shaft support part and supplies lubricating oil to an oil port of the in-shaft oil passage that opens on the axial side surface of the shaft support part, the oil reservoir A forced lubrication mechanism for a planetary gear device, characterized in that the forced lubrication mechanism is installed between the side surface of the shaft support and an oil seal material.