JPH0689817B2 - Forced lubrication device for planetary funnel system - Google Patents

Description

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

[Prior Art] An automatic transmission changes gears by changing the power transmission path by connecting and changing the speed change elements of a plurality of planetary gear devices by engaging and releasing friction engagement elements. Among the transmission elements, the pinion that constitutes the transmission gear is a transmission element that frequently rotates at a high speed because it is constantly driven to rotate and is involved in power transmission when the vehicle equipped with an automatic transmission is running, except in the direct connection state. . Therefore, it is not unthinkable to provide an oil passage in the carrier that communicates from the speed change shaft to the rotation support portion of the pinion for forced lubrication, but as is known, there is a demand for a compact automatic transmission. The axial length and the outer diameter are designed to be reduced as much as possible, and it is said that the arrangement of the mechanism inside the transmission is made as close as possible due to the requirement of multiple stages. Since the shaft support portion of the carrier 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 inside the shaft that connects the axial end surface and the outer peripheral surface, the oil duct is attached to the side surface of the shaft support, and the oil passage injection port formed on the shaft of the sun gear is connected to the oil passage. Lubricating means has been proposed that opens toward the opening of the duct and receives the oil discharged from the injection hole of the sun gear shaft by the oil duct and guides it to the rotation support portion of the pinion gear (Shokai Sho 58-
67161).

[Problems to be solved by the invention]

However, the sun gear shaft, which is the shift shaft of the automatic transmission, and the carrier provided with the shaft support are inevitably assembled so as to allow some movement (backlash) in the axial direction. With the lubrication means used, the above positional relationship is not always maintained accurately, and it is difficult for the oil duct to receive the entire amount of ejected oil, and there is a risk that oil will not be sufficiently supplied into the opening of the oil duct. was there.

By the way, the present applicant has previously made the thrust bearing lubricant thrust between the shaft support and the member disposed adjacent to the shaft support function as a guide to lubricate the thrust bearing. Has been proposed so as to direct the oil to the opening of the oil reservoir to efficiently lubricate both the thrust bearing and the rotation support portion of the pinion.

In order to further ensure the function of this device, the present invention eliminates oil leakage from the thrust bearing by eliminating a gap between the thrust trace of the thrust bearing and the adjacent member abutting it. To solve the above-mentioned problem of insufficient lubrication of the transmission gear rotation support bearing in the automatic transmission by ensuring the sufficient function of the race guide and ensuring sufficient supply of lubricating oil to the oil reservoir. The purpose is.

[Means for Solving the Problems] In order to achieve the above object, the present invention provides a pinion shaft which is disposed on a shaft and rotatably supports a ring gear, a pinion gear, a sun gear, and the pinion gear via a bearing. And a planetary gear device having a carrier that supports the pinion shaft, an outer peripheral discharge oil passage formed on the shaft, and a shaft from an axial end of the pinion shaft to guide lubricating oil from the outer peripheral discharge oil passage to the bearing. A forced lubrication device for a planetary gear device, comprising: an in-shaft oil passage formed inwardly; and an oil reservoir provided at an axial end of the pinion shaft to guide lubricating oil to the in-shaft oil passage. A guide bent in the direction away from the axial end of the pinion shaft is formed on the inner circumference of the A thrust bearing is disposed between the ring gear and the sun gear on the inner side and on the outer side in the radial direction of the outer peripheral discharge oil passage, and the thrust bearing is provided on the outer periphery of the thrust race toward the pinion shaft support portion side. A bent portion that bends in the axial direction is formed, the guide portion and the bent portion overlap in the axial direction, and the thrust bearing is pressed by the axial force that acts between the ring gear and the sun gear. Each tooth profile of the sun gear, the pinion gear, and the ring gear is formed as a helical tooth.

[Operation and effect of the invention]

In the forced lubrication device according to the present invention configured as described above, the axial force is applied to the ring gear and the sun gear by the helical teeth formed in each gear of the planetary gear device during power transmission. As a result, the thrust bearings located between them are pressed, and the thrust traces of the thrust bearings are pressed against the ring gear by this pressing force, preventing the formation of a gap between the thrust traces and the ring gear. Therefore, almost all the oil discharged from the outer peripheral discharge oil passage provided on the shaft with the rotation of the shaft enters the thrust bearing and is guided by the bent portion of the thrust trace overlapping the guide portion of the oil reservoir. It is surely introduced into the reservoir. Therefore, a sufficient amount of oil can be used to lubricate the bearing of the pinion gear rotation support portion.

When the forced lubrication device of the present invention having the above-described configuration is applied to a planetary gear device that is operated under conditions where oil supply from the sun gear side cannot be expected, such as the planetary gear rotating at high speed with the sun gear stopped. It works extremely effectively.

〔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 plate-shaped rear cover 202 welded to the inner periphery thereof, a pump impeller 203 provided on the inner peripheral wall of the rear cover 202,
A turbine shell 205 holding a turbine runner 204 arranged to face the pump impeller 203 is supported by a fixed shaft 207 connected to the transmission case 110 via a one-way clutch to provide torque capacity when the input speed is low. A stator 208 to be increased, a direct coupling clutch (lock-up clutch) 209 arranged between the front cover 201 and the turbine shell 205 and directly coupling them are provided.

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 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.
Reference numeral 11 denotes a rearward-facing hole into which the tip is inserted into the hole 102 of the input shaft 10 and has a flange portion 111 at the rear end, and the tip of the output shaft 12 that transmits power to the drive wheel side is inserted into the center. Equipped with 112. The output shaft 12 has an extension housing 14
A sensor rotor 121 for detecting the number of revolutions and a speedometer drive gear 122 are fixed in 0, and a spline groove 123 is formed on the outer periphery at the rear end to dry the sleeve yoke that transmits power to the drive wheels. The output shaft 12 is rotatably supported by the extension housing 140 via a sleeve yoke, and the front side thereof is an intermediate transmission shaft.
It is rotatably supported by the inside of the hole 112 of 11 and the inner circumference of the rear support 133.

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.
The second support portion 131 is rotatably fitted and provided between the outer peripheral wall 20A and the inner peripheral wall 20B, and the annular piston 21 that presses the clutch C2 is fitted between the outer peripheral wall 20A and the inner peripheral wall 20B. A hydraulic servo C-2 of the clutch C2 is formed between the servo drums 20, and a return spring 22 for pressing the annular piston 21 to the hydraulic servo C-2 side is attached to the inner peripheral wall 20B side, and an inner side of the outer peripheral wall 20A is attached. Clutch C2 is attached to. 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
The pinion shaft 4A that rotatably supports via the bearing roller 2A held by the cage 2B, and both axial end surfaces of the pinion gear 2 via the 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
A rotation support member that rotatably supports the outer circumference of 12, that is, an annular protrusion that is provided so as to project in front of the ring gear support member 27.
It is connected to the third hydraulic servo drum 24 via 28 and the clutch C1.

In the present embodiment, the second planetary gear device U1 outputs the power of the intermediate transmission shaft 11 transmitted to the ring gear 3 via the clutch C1 during forward traveling of the vehicle and coupled to the carrier 4 by another engagement element. It is provided to output to the shaft 12. As a result, the ring gear 3 is automatically moved by the automatic transmission 10 when the vehicle travels forward.
It receives the power transmission in the counterclockwise direction when viewed from the viewpoint of the output side of 0.
The second planetary gear unit U1 has a tooth profile of the ring gear 3 that is configured to provide a force for moving the ring gear 3 backward and the sun gear 1 forward when the vehicle travels forward.
The output side of 100 is an helical bevel with an inner circumference of about 25 ° from the output side to the right side. The pinion gear 2 and the sun gear 1 are helical gears corresponding to the helical teeth of the ring gear 3. It is said that. Then, the pinion carrier 4 is formed with an in-shaft oil passage 4E that passes through the pinion shaft 4A from the axial end surface 4C on the shaft support portion 4B side of the pinion shaft 4A to the center of the inner circumference 4D of the pinion shaft 4A. A cutting groove 4H is formed on the inner peripheral side from the oil port 4G on the axial end surface 4C of the oil passage 4E. On the front end surface of the shaft support 4B, an oil port
With the inner circumference open so that lubricating oil can be stored in 4G, the outer circumference is locked to the end circle of the shaft support 4B and the oil reservoir
4F is provided. FIGS. 3 and 4 show the shape of the oil reservoir 4F. As shown in this figure, the oil reservoir 4F is made of a press-molded product and is formed into an annular shape so that it can be brought into contact with the end surface of the carrier 4. It is configured to be fixed. Therefore, the oil server 4F is provided with claws 4J for caulking the outer circumference of the carrier 4 at four locations on the outer circumference thereof, and at four intermediate diameter portions facing the end face of the pinion shaft 4A when the carrier 4 is attached to the oil 4a. , A bulging portion 4L is formed to form an oil inflow path between the end surface and
Furthermore, on the inner circumference, the pinion shaft 4A is used for the entire circumference.
A guide portion 4K bent in a direction away from the end face is formed so as to form an opening for taking in oil between the end face and the end face.

Between the shaft support portion 4B and the ring gear support member 27,
A thrust bearing 5 is interposed so that they can rotate relative to each other. A thrust race 5A on the front side thereof abuts a ring gear support member 27 which is an adjacent member, and a thrust race 5B on the rear side is a shaft support portion. It is in contact with 4B.
The flange portion 5C on the outer peripheral side of the thrust trace 5A is formed with a bent portion bent in the axial direction toward the shaft support portion 4B so as to overlap with 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 ring gear support member 27, and the output shaft
It faces the outer peripheral discharge oil passage 6A for supplying lubricating oil between the shaft support portion 4B and the ring gear support member 27 from the in-shaft lubricating oil supply oil passage 12A in the ring gear support member 27 and the bearing 5 The thrust trace 5A is provided with a projecting portion 27A protruding rearward so as to support the thrust trace 5A on the outer peripheral side.

In the device of this embodiment, the power from the engine is the clutch.
When it is input to the ring gear 3 via C1 and is output to the carrier 4 via the pinion gear 2 by the load applied to the sun gear 1, the ring gear 3 is formed by the helical teeth formed on each gear of the planetary gear unit U1. To the sun gear 1 and forward to the sun gear 1. As a result, the ring gear supporting member 27 and the sun gear 1 press the shaft supporting portion 4B arranged between them and the bearings 5 and the bearings 6 arranged before and after the shaft supporting portion 4B. The front surface of the thrust trace 5A is crimped to the rear surface of the ring gear support member 27 to prevent the formation of a gap between the thrust trace 5A and the ring gear support member 27 which is an adjacent member.

The supply of lubricating oil to this forced lubrication mechanism is performed 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 centrifugally or hydraulically applied from the outer peripheral discharge oil passage 6A to the shaft support portion 4B and the ring gear support member 27.
In between. The discharged oil will be
Bearing 5 arranged between 4B and ring gear support member 27
Is lubricated, is squeezed by the clearance A, flows out to the outer peripheral side, and is collected in the opening of the oil reservoir 4F. Oil reservoir 4F
The oil collected therein 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 flowing between the pinion gear 2 and the pinion shaft 4A forcibly lubricates the pairing 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. Is fixed to the outer circumference of the second planetary gear unit U.
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. Furthermore f
Indicates that the corresponding one-way clutch is free.

As described in detail above, according to the device of this embodiment, the thrust traces 5A are brought into pressure contact with the ring gear support member 27 by the pressing force applied to the shaft support portion 4B and the ring gear support member 27 and the ring gear support member 27. In order to prevent the formation of the gap between the thrust traces 5A, the oil discharged from the outer peripheral discharge oil passage 6A of the speed change shaft 12 is surely supplied to the bearings 5, and the oil that lubricates the bearings 5 is absorbed by the thrust traces 5A.
Since it is deflected and guided by the flange 5C and effectively collected in the oil reservoir 4F, a sufficient amount of lubricating oil is supplied to the oil port of the shaft internal oil passage 4E, and an effective forced lubrication effect can be obtained. Of.

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), 6A …… outer peripheral oil passage, 12 …… output shaft,

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 inner side of the oil reservoir and the outer side of the outer peripheral discharge oil passage are provided with the guide portion. A thrust bearing is disposed between the gear and the sun gear, and a thrust portion of the thrust bearing is formed with a bent portion that is bent in the axial direction toward the pinion shaft support portion side, and the guide portion and the bent portion are formed. And the tooth profile of the sun gear, the pinion gear, and the ring gear are formed on the helical teeth so as to press the thrust bearing by the axial force acting between the ring gear and the sun gear. A forced lubrication device for a planetary gear device.