JPH0561496B2 - - Google Patents

Description

[Detailed description of the invention]

[Industrial Field of Application] The present invention relates to the lubrication of automatic transmission bushes. [Prior Art] Conventionally, a central shaft having a lubricating oil passage therein, a cylindrical member attached to the outer periphery of the central shaft by spline fitting, and a cylindrical member attached to the outer periphery of the central shaft and the cylindrical member. , an inner encasing member circumferentially enclosing the central axis and the cylindrical member; an oil seal disposed between the central axis and the inner encasing member; and an oil seal disposed between the cylindrical member and the inner encasing member. a bush, an annular chamber surrounded by the central shaft, the cylindrical member, the inner housing member, the oil seal, and the bush, and lubricating oil is supplied to the chamber from the oil passage in the central shaft. In the bushing lubrication mechanism consisting of an oil passage, the inner spline on the outer periphery of the central shaft and the outer spline on the inner periphery of the cylindrical member are spline fitted, so there is no spline fitting between the central shaft and the cylindrical member. A gap was formed between the two. [Problems to be Solved by the Invention] As described above, since a gap is formed between the central shaft and the cylindrical member, the lubricating oil supplied to the chamber from the oil passage flows into the gap, causing the bushing to be damaged. There was a risk that insufficient lubrication would occur. Therefore, in order to prevent the lubricating oil from flowing out, it is conceivable to arrange, for example, an oil seal between the central shaft and the cylindrical member. However, simply arranging an oil seal or the like requires a space for it, resulting in a problem that the axial dimension becomes longer. SUMMARY OF THE INVENTION Therefore, an object of the present invention is to provide a lubrication mechanism for an automatic transmission that can reliably supply lubricating oil from a lubricating oil passage in a central shaft to a bushing without increasing the axial dimension. [Means for Solving the Problems] In order to solve the above problems, the present invention provides a central shaft having a lubricating oil passage therein, a flange member supporting a ring gear of a planetary gear device, and a central shaft of the central shaft. a connecting member having a cylindrical member that is spline-fitted and attached to an outer periphery; an inner enclosing member that circumferentially encloses the central axis and the cylindrical member on the outer periphery of the central axis and the cylindrical member; A bearing disposed between the inner envelope member and the flange member, an oil seal disposed between the central shaft and the inner envelope member, and a bush disposed between the cylindrical member and the inner envelope member. The central shaft has an oil passage provided radially outward from the lubricating oil passage in the central shaft for supplying lubricating oil to the bush, and a stepped portion that abuts the cylindrical member. an annular chamber is formed by bringing the cylindrical member into contact with the inner packaging member, the oil seal, the bush, and the stepped portion, and lubricating oil is supplied to the bush through the chamber. has. [Operation and Effects of the Invention] With the above configuration, the present invention can reliably transmit power by spline fitting the connecting member to the central shaft, and further includes a stepped portion on the central shaft that abuts the cylindrical member. forming the inner packaging member, oil seal,
An annular chamber is formed by bringing the cylindrical member into contact with the bush and the stepped portion, and lubricating oil is supplied to the bush through the chamber, so for example, an oil seal etc. The lubricating oil can be reliably supplied to the bush without increasing the axial dimension due to the arrangement, and the durability of the bush can be improved. In addition, the ring gear of the planetary gear system causes rattling between the ring gear and the pinion gear due to the error of the helical gear, but since the clearance between the central shaft and the cylindrical member is small, rattling can be prevented and noise generation can be prevented. [Embodiment] Next, a lubrication mechanism for an automatic transmission according to the present invention will be explained based on an embodiment shown in the drawings. FIG. 1 is a cross-sectional view showing a lubrication mechanism for an automatic transmission according to the present invention, and FIG. 2 is a cross-sectional view of a vehicle automatic transmission to which the automatic transmission lubrication mechanism according to the present invention is applied. The automatic transmission 100 includes a hydraulic torque converter 200, a transmission 300, and a hydraulic control device 400. The transmission 300 includes an overdrive transmission 300A comprising a first planetary gear unit U0, one multi-disc clutch C0 operated by a hydraulic servo, one multi-disc brake B0, and one one-way clutch F0; 2 Planetary gear unit U
1. Third planetary gear unit U2, two multi-disc clutches C1 and C2 operated by hydraulic servo, one belt brake B1, two multi-disc brakes B2,
B3, and two one-way clutches F1, F2
The underdrive transmission 300B has three forward speeds and one reverse speed. A transmission case 110 of the automatic transmission 100 is a transmission 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. It consists of a case 130 and an extension housing 140 that covers the rear side of the automatic transmission 100, and these torque converter housings 1
20, transmission case 130, and extension housing 140 are each fastened with a large number of bolts. The torque converter 200 has a torque converter housing 120 that is open at the front (engine side).
A front cover 201 is housed in the interior and rotates under the drive of an engine (not shown); a circular plate-shaped rear cover 202 welded to the inner periphery of the front cover 201; a pump impeller 203, a turbine runner 204 disposed opposite the pump impeller 203, a turbine shell 205 holding the turbine runner 204, and a one-way clutch 206.
A stator 208 is supported by a fixed shaft 207 connected to the transmission case 110 and increases the torque capacity when the input rotation speed is low, and a stator 208 is connected to the front cover 201 and the turbine shell 205 between the front cover 201 and the turbine shell 205. A lock-up clutch 209 is provided that rotates the shell 205 at the same time. An external gear 150 is disposed inside the torque converter housing 120 and a cylindrical transmission case 130 continuous to the rear of the torque converter housing 120.
an oil pump housing 152 that houses an internal gear oil pump 150 having an internal gear a and an internal gear 150b, and has a cylindrical part 151 that protrudes forward on the inner periphery;
is fastened to the front part of the transmission case 130, and an extension member 210 connected to the inner circumferential end of the rear cover 202 is spline-fitted to the inner circumference of the external gear 150a via the inner circumference of the cylindrical part 151. ing. Further, a foil 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 housing 152, so that the oil pump housing 152 and the foil pump cover 1
54 forms a partition wall between the torque converter housing 120 and the transmission case 130. Further, in the middle of the transmission case 130, a rearwardly protruding cylinder 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 shaped support portion 131 is provided. At the rear of the transmission case 130 (on the right side in the drawing), there is provided an internal enclosing member 3 having a cylindrical boss portion 3A projecting forward and enclosing a central shaft 1 and a cylindrical member 2 described below in the circumferential direction. It is being A fixed shaft 207 of a one-way clutch 206 that supports a stator 208 of a torque converter 200 is fitted inside the front support 153.
A torque converter 200 is installed inside the fixed shaft 207.
The input shaft 10 of the transmission 300, which is the output shaft of the transmission 300, is rotatably supported. The input shaft 1
0 has a flange portion 101 at the rear end, and a rearward hole 102 is formed in the center of the rear end.
An intermediate 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 transmission shaft 11 is connected to the input shaft 10.
The intermediate transmission shaft 11 has a flange portion 111 at its rear end, and the tip of the central shaft 1, which is an output shaft for transmitting the power of the present invention to the drive wheels, slides in the center of the intermediate transmission shaft 11. A rearward facing hole 112 is formed. A lubricating oil supply path 1A is provided inside the central shaft 1 to supply lubricating oil to each part. The center shaft 1 has a sensor rotor 121 for detecting rotational speed and a speedometer drive gear 122 fixed in the extension housing 140, and the rear end has a sleeve yoke attached to the outer periphery for transmitting power to the drive wheels. A spline groove 123 is formed, and the sleeve yoke is rotatably supported by an extension housing jig 140, and the front end is rotatably supported within the hole 112 of the intermediate transmission shaft 11. In the overdrive transmission 300A, a first planetary gear unit U0 is provided behind the input shaft 10, a ring gear R0 thereof is connected to the intermediate transmission shaft 11 via a flange plate 113, and a planetary carrier P0 is connected to the input shaft 10. 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 device U0, there is a first
A hydraulic servo drum 14 is fixed to the inner race shaft 13, and the outer peripheral wall 1 of the first hydraulic servo drum 14 is fixed to the inner race shaft 13.
An annular piston 15 is fitted between the inner peripheral wall 14A and the inner peripheral wall 14B to form a hydraulic servo C-0 of a clutch C0 that engages and disengages the carrier P0 and the first hydraulic servo drum 14.
A return spring 16 that presses the annular piston 15 toward the hydraulic servo C-0 side and an outer peripheral wall 14B on the 3 side.
A clutch C0 is attached to the inside of the clutch C0.
0, the first hydraulic servo drum 14 and the inner race shaft 13 are connected to the carrier P0. A one-way clutch F0 having the inner race shaft 13 as an inner race is provided on the inner periphery of the first hydraulic servo drum 14, and a clutch C0 and a brake B0 are provided on the outer periphery between the outer race 17 and the transmission case 130. , a piston 18 that presses the brake B0 is fitted in front of the center support 132 at the rear of the brake B0, and a hydraulic servo B-0 of the brake B0 is formed between the piston 18 and the center support 132,
Front end inner peripheral part 135 of center support 132
A return spring 19 that presses the piston 18 toward the hydraulic servo B-0 is fitted therein. The underdrive transmission 300B includes, at the front, a second hydraulic servo drum 20 that opens rearward.
is rotatably fitted on the outer periphery of the support portion 131 of the center support 132, and an annular piston 21 that presses the clutch C2 is fitted between the outer circumferential wall 20A and the inner circumferential wall 20B, and the annular piston 21 and the second
A return spring 22 forms the hydraulic servo C-2 of the clutch C2 between the hydraulic servo drum 20 and presses the annular piston 21 toward the hydraulic servo C-2 on the inner peripheral wall 20B side, and the clutch C2 is located inside the outer peripheral wall 20A. It is installed. Behind the second hydraulic servo drum 20, a third hydraulic servo drum 24, which is open to the rear and has an annular protrusion 23 at the front, is fixed to the outer periphery of the flange portion 111 at the rear of the intermediate transmission shaft 11. The rear end of the shaft 11 and the outer peripheral wall 24 of the third hydraulic servo drum 24
A clutch C1 is installed between the outer circumference of the flange portion 111 and the
An annular piston 25 for pressing the clutch C1 is fitted to form a hydraulic servo C-1 of the clutch C1 between the annular piston 25 and the third hydraulic servo drum 24, and an annular piston 25 and a hydraulic servo C-1 are formed on the inner circumferential side of the clutch C1. A return spring 26 presses toward the 1st side, and a clutch C2 is attached to the outer periphery of the annular protrusion 23.
is attached, and the second and third hydraulic servo drums 20 and 24 are connected via a clutch C2. A second planetary gear device U1 is provided behind the third hydraulic servo drum 24, and a ring gear R thereof is provided in front of a rotation support member 27 that rotatably supports the ring gear R1 on the outer periphery of the central shaft 1. The third
The carrier P1 is connected to the hydraulic servo drum 24.
is spline-fitted to the front end of the central shaft 1, and the sun gear S1 is integrally formed at the end of a sun gear shaft 29 rotatably provided on the outer periphery of the central shaft 1. In addition, the second and third hydraulic servo drums 2
0, 24 and the second planetary gear unit U1 in a minimum space.
A belt whose front end is fixed to the outer periphery of the second hydraulic servo drum 20, whose rear end is connected to the sun gear shaft 29 on the rear side of the second planetary gear unit U1, and which fixes and releases the connecting drum 30 on the outer periphery side. A brake B1 is provided. A spline 136 formed inside the transmission case 130 has a front brake B2.
Brake plate B2, rear brake plate B3
The brake plate b3 of is spline fitted,
A fourth hydraulic servo drum 32, which opens forward and has an annular projection 31 on the front side, is spline-fitted between the brakes B2 and B3. An annular piston 33 for hydraulically applying brake B2 is fitted between the outer peripheral wall 32A of the fourth hydraulic servo drum 32 and the annular projection 31, and the annular piston 33 and the fourth
The hydraulic servo B-2 of the brake B2 is formed between the hydraulic servo drums 32, and the inner peripheral wall 32B
A return spring 34 is provided on the side to press the annular piston 33 toward the hydraulic servo B-2. In addition, the sun gear shaft 2 is located on the inner circumferential side of the brake B2.
A one-way clutch F1 having an inner race 9 is provided, and a brake B2 is provided on the outer periphery of the outer race 35. An annular hole 36 formed between the outer peripheral side of the boss portion 3A of the rear support wall 134 on the rear side of the brake B2 and the transmission case 130.
A plurality of pistons 37 that press the brake B3 to
1,373 and the reaction sleeve 372 are fitted to form the hydraulic servo B-3 of the brake B3, and the pistons 371, 373 are fitted to the hydraulic servo B-3.
A return spring 38 that presses toward the −3 side is supported by a return spring fixture 38A attached to the tip of the boss portion 3A. The inner race 39 of the one-way clutch F2 disposed on the inner circumference of the brake B3 is connected to the fourth hydraulic servo drum 32 on the outer circumference of the sun gear shaft 29, and the brake B3 is attached to the outer circumference of the outer race 40 of the one-way clutch F2. ing. The third planetary gear device U2 is a sun gear S2
is formed integrally with the sun gear shaft 29, and the carrier P
2 is the outer race 4 of the front one-way clutch F2
0 and also connected to brake B3,
A ring gear R2 having a parking gear 41 disposed around the outer periphery is connected to the outer periphery of the central shaft 1 via a connecting member 42 fitted with a spline. The parking gear 41 is provided so that when the shift lever of the automatic transmission is selected to the parking P position, a parking pawl 43 meshes with the parking gear 41 to fix the center shaft 1. The connecting member 42 is an annular flange 2A that supports the ring gear R2 in the circumferential direction.
and a cylindrical member 2 that is spline-fitted to the outer periphery of the central shaft 1. The cylindrical member 2 is fitted inside the boss portion 3A of the inner packaging member 3, and the cylindrical portion 2 and the boss portion 3A There is a groove 5A that communicates with the inner circumferential side in the axial direction.
A bushing 5 is interposed therebetween. Further, a stepped portion A is formed on the central shaft 1, and the cylindrical member 2 of the connecting member 42 is brought into contact with the stepped portion A, so that a small clearance is maintained between the central shaft 1 and the cylindrical member 2. .
After the cylindrical member 2, a central shaft is supported by a rotating shaft on the inner periphery of an inner envelope member 3 via an oil seal 4.
Central shaft 1, cylindrical member 2, boss portion 3 of inner envelope member 3
A chamber 6 is formed between each of the oil seal 4 and the bush 5, and an oil passage 7 for supplying lubricating oil from the lubricating oil supply passage 1A in the central shaft 1 to the chamber 6 is provided. Lubricating oil is supplied into the chamber 6 via the oil passage 7 due to the rotation of the central shaft 1 and the oil pressure of the lubricating oil supply passage 1A. The lubricating oil supplied into the chamber 6 forms a step A on the central axis 1, and connects the connecting member 42 to the step A.
Since the cylindrical member 2 is brought into contact with the central shaft 1, the clearance between the central shaft 1 and the cylindrical member 2 is reduced, and most of the lubricating oil supplied into the chamber 6 is reliably delivered to the oil seal 4 and the bushing. 5, the durability of the bush 5 can be improved. Further, the lubricating oil supplied to the bush 5 side flows out to the annular flange 2A side of the connecting member 42 through the groove 5A provided on the inner circumference of the bush 5, and is disposed between the annular flange 2A and the boss portion 3A. It is supplied to the roll bearing 8 and the outer periphery of the roll bearing 8, and lubricates each member on the outer periphery. The transmission 300 operates according to vehicle running conditions such as vehicle speed and throttle opening from a hydraulic control device 400 in a valve body 403 built into an oil pan 402 fastened to the lower part of the transmission case 130 with bolts 401. The hydraulic pressure selectively output to the hydraulic servo of the frictional engagement device engages or releases each clutch and brake, resulting in four forward speeds or one reverse speed change. Table 1 shows an example of the operation of each clutch, brake, and one-way clutch and the achieved gear position (RANGE).

【table】

[Table] In Table 1, E indicates that the corresponding clutch or brake is engaged. × indicates that the corresponding clutch and brake are released.
The corresponding one-way clutch of L is engaged in the engine drive state, but this engagement is not necessarily required as power transmission is guaranteed by the clutch or brake built in parallel. Indicates that (lock). L indicates that the corresponding one-way clutch is engaged only in engine drive conditions and not in engine brake conditions. Furthermore, 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 lubrication mechanism for an automatic transmission according to the present invention, and FIG. 2 is a cross-sectional view of a vehicle automatic transmission to which the automatic transmission lubrication mechanism according to the present invention is applied. DESCRIPTION OF SYMBOLS 1... Central axis, 1A... Lubricating oil path, 2... Cylindrical member, 2A... Flange member, 3... Inner enclosure member,
4...Oil seal, 5...Butsuyu, 5A...
Oil groove, 6... Chamber, 7... Oil path, 8... Bearing, 42... Connection member, R2... Ring gear.

Claims (1)

[Scope of Claims] 1. A central shaft having a lubricating oil passage therein, a flange member supporting a ring gear of a planetary gear device, and a cylindrical member spline-fitted and attached to the outer periphery of the central shaft. a connecting member; an inner casing member that circumferentially encloses the central shaft and the cylindrical member on the outer periphery of the central shaft and the cylindrical member; and a bearing disposed between the inner casing member and the flange member; , an oil seal disposed between the central shaft and the internal packaging member, and a bushing disposed between the cylindrical member and the internal packaging member, the central shaft supplying lubricating oil to the bush. an oil passage provided radially outward from the lubricating oil passage in the central shaft, and a stepped portion that abuts the cylindrical member; A lubrication mechanism for an automatic transmission, characterized in that an annular chamber is formed by bringing the cylindrical member into contact with the stepped portion, and lubricating oil is supplied to the bush through the chamber. 2. Claim 1, wherein the bush is provided with an oil groove communicating in the axial direction on the inner periphery or the outer periphery, and lubricating oil supplied from the chamber is supplied to the bearing via the oil groove. Lubricating mechanism for automatic transmission as described in Section 1.