JPH0536647B2 - - Google Patents

Abstract

PURPOSE:To make it possible to assemble a shell-type needle roller bearing without using any special jig, by forming a tapered surface having a width 15% or more of a thickness of a shell and an angle of 10 deg. to 30 deg. on an inside diameter side of at least one of folded portions formed at outside both ends. CONSTITUTION:A shell-type needle roller bearing 1 is formed with folded portions 2A and 2B at both ends of a cylindrical shell 2. The folded portion 2A engaged with the bearing upon assembling is formed on the inner diameter side with a tapered surface 2C having a width 15% or more of a thickness of the shell 2 and an angle theta of 10 deg. to 30 deg.. When the shell-type needle roller bearing 1 is engaged with another member rotatably supported to a hollow rotating shaft, the tapered surface 2C urges a seal ring engaged with an outer surface of the another member to smoothly fit the seal ring into a seal ring groove, thereby smoothening engagement of the hollow rotating shaft.

Description

[Detailed description of the invention]

[Industrial Field of Application] The present invention relates to a vehicular automatic transmission equipped with a shell-type needle roller bearing. [Prior Art] In general, in automatic transmissions for vehicles, there are many parts in which shell-type needle roller bearings are used between two relatively rotating members. Radial holes are formed in these members as oil supply and drainage passages for hydraulic oil or lubricating oil, and
An oil seal ring is disposed between the shell type needle roller bearing and the front air hole. On the other hand, in recent years, as this oil seal ring,
The use of seal rings made of resins such as Teflon (product: polychloro trifluoro ethylene) is being considered for the purpose of improving sealing performance, reducing the coefficient of friction, and reducing weight. [Problems to be Solved by the Invention] When assembling the automatic transmission for a vehicle as described above, it has not been conventionally done to assemble a shell-type needle roller bearing by climbing over a seal ring disposed on the shaft. However, in order to simplify the assembly procedure, there are cases where it is desired to assemble a shell-type needle roller bearing by climbing over the seal ring, but with conventional shell-type needle roller bearings, when passing through the seal ring, the shell-type needle roller bearing Roller bearings can easily cause scratches on the seal ring surface, which may cause a reduction in sealing performance. This problem is particularly serious when using a relatively soft resin oil seal ring as described above. Therefore, the only way to assemble is to use a special jig. The present invention has been made in view of the above circumstances, and its purpose is to mount the oil seal ring without using any special assembly jig and without damaging the surface of the oil seal ring. The present invention aims to provide an automatic transmission equipped with a shell-type needle roller bearing that can be assembled by climbing over a ring. [Means for Solving the Problems] In order to solve the above object, the present invention includes a rotating shaft, a seal ring disposed in a groove carved in the rotating shaft, and a shell-type needle roller bearing that supports the rotary shaft disposed on the inner diameter side of the fixation member in a relatively rotatable manner and is assembled over the seal ring, the shell-type needle roller bearing The roller bearing includes a cylindrical shell fixed to the inner diameter side of the fixing member, a bent portion formed at both ends of the cylindrical shell, and a plurality of openings with both ends locked to the bent portion. a roller which is rotatably loosely fitted into the opening of the gauge and rotatably supports the rotating shaft, the supporting surface of which is formed to have a smaller diameter than the bent portion and the tip; A tapered surface is formed on the inner diameter side of at least one bent portion so as to be brought into contact with the outer circumferential portion of the seal ring during assembly so that the extension line does not intersect the outer circumferential surface of the roller. [Operations and Effects of the Invention] In the automatic transmission for vehicles of the present invention configured as described above, when the shell-type needle roller bearing is assembled, the tapered surface smoothly squeezes the seal ring inward, and the seal ring fits into the groove. It passes around the outer circumference of the seal ring while being pushed inward. Therefore, without using any special assembly jig,
A shell type needle roller bearing can be assembled through the seal ring without damaging the surface of the seal ring. In addition, this assembly work can be performed without any special assembly jig or tools.
Highly easy to assemble. Further, by providing tapered surfaces at both ends of the cylindrical shell, both attachment and detachment operations can be smoothly performed in the same operation as described above. [Example] The present invention will be described below based on an example shown in the drawings. FIGS. 2 and 3 are cross-sectional views showing one embodiment of an automatic transmission according to the present invention. The automatic transmission 100 includes a fluid transmission device (torque converter in this embodiment) 200, a transmission 300, and a hydraulic control device 400. The transmission 300 includes a first planetary gear set p1, 1 operated by a hydraulic servo.
1 multi-disc clutch C0, 1 multi-disc brake B
0, and an overdrive planetary gear transmission 10 with one one-way clutch F0, a second planetary gear set p2, a third planetary gear set p3, two multi-disc clutches C1, C2, 1 operated by hydraulic servos. Two belt brakes B
1. An underdrive planetary gear transmission 40 with three forward speeds and one reverse speed, comprising two multi-plate brakes B2, B3 and two one-way clutches F1, F2.
It consists of An automatic transmission case 110 includes a torque converter housing 120 that houses a torque converter 200 and an overdrive planetary gear transmission 10.
and an underdrive planetary gear transmission 40 in series.
0, 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 each have a coaxial center with a large number of bolts. It has been concluded as follows. The torque converter 200 has the torque converter housing 1 opened at the front (engine side).
The front cover 11 is housed in the torque converter chamber 121 of 20 and is connected to the engine departure shaft.
1. An annular plate-shaped rear cover 112 welded to the front cover 111 at the outer periphery; the rear cover 11;
2, a turbine runner 206 disposed opposite the pump impeller 205, a turbine shell 207 holding the turbine runner 206, and a one-way clutch 202. It consists of a stator 201 supported by a fixed shaft 203 via a stator 201, and an annular plate-shaped clutch disk 50 whose inner periphery is connected to a friction surface 20 provided on the inner surface of the front cover 111 and a turbine hub 208 which is an output member. , a lock-up clutch 113 that directly connects the front cover 111 and the turbine shell 207 is provided. The torque converter chamber 121 and the cylindrical transmission chamber 132 of the transmission case 130 continuous to the rear thereof.
A gear-type oil pump 150 is housed therebetween, and an oil pump body 151 having a cylindrical portion 152 protruding forward at the center is fitted into the front end of the transmission case 130. The cylindrical portion 152 is fastened to the rear side of the oil pump body 151.
an oil pump cover 1 having a cylindrical front support 153 which has a coaxial core and which protrudes rearward;
54 is fastened. The oil pump body 151 and the oil pump cover 154 form an oil pump housing 155, which serves as a partition wall between the torque converter chamber 121 and the transmission chamber 132, and also serves as a front support wall of the transmission. Further, in the middle of the transmission chamber 132, there is a center support 158 that is a cylindrical co-rotating shaft that projects rearward, and an intermediate support wall 159 that separates the overdrive mechanism chamber 133 and the underdrive mechanism chamber 134.
is cast separately and installed by fitting. Furthermore, at the rear of the transmission case 130, there is a cylindrical rear support 1 that protrudes forward.
A rear support wall 157 having a diameter of 56 is provided by integral casting. A stainless steel sleeve 6 having a radial oil hole 5A and seal ring grooves 5B, 5C on both sides thereof is fitted onto the outer periphery of the center support 158, and these seal ring grooves 5B, 5C are made of Teflon. Synthetic resin seal rings 5D and 5E mainly made of are fitted. Further, a bush (metal bearing) 7 is fitted in the front part of the inner periphery of the front air center support 158, and a shell type needle roller bearing 1, which will be described later, is fitted in the rear part. The oil pump housing (bulkhead or front support wall) 1
55 and the rear support wall 157 forms a transmission chamber 132, and between the rear support wall 157 and the extension housing 140 forms an output shaft chamber 141 of the transmission. Type sensor rotor 143, speed meter live gear 1
44 is fixed to the output shaft, and a sleeve yoke having a coaxial center with the front support 153 at the rear end and spline-fitted to the outer periphery of the output shaft end is inserted through the sleeve yoke. A fixed shaft 203 of the one-way clutch 202 that supports the stator 201 of the torque converter 200 is fitted inside the front support 153, and the torque converter 2 is fitted inside the fixed shaft 203.
The input shaft 11 of the transmission, which is the output shaft of 00, is rotatably supported. The input shaft 11
is the flange part 1 behind the front support 153.
2a, the rear end portion 12 is formed with a slightly larger diameter,
A rearward-facing central hole 13 is formed in the axis of the rear end portion 12 . Behind the input shaft 11, an intermediate transmission shaft 14, which is a fixed member having a coaxial core and arranged in series with the input shaft 11, is connected to the center support 158.
It is rotatably supported and arranged. The intermediate power transmission shaft 14 has its tip inserted into the center hole 13 and comes into sliding contact with the inner circumferential wall of the center hole via a thrust bearing, and the rear end 15 of the intermediate power transmission shaft 14 has a large diameter, A rearward-facing center hole 16 is formed into which the tip of the output shaft 36 is inserted and makes sliding contact. On the fitting surface between the intermediate transmission shaft 14 and the center support 158, there is a bush 7 on the center support 158.
is fitted inside, and two radial oil holes 7A and 7B are provided in the intermediate transmission shaft 14, and oil seal grooves 7C, 7D, and 7E are formed on both sides of each hole, and these oil seal grooves 7C, 7D, Seal rings 7F, 7G, and 7H made of synthetic resin mainly made of Teflon are fitted into 7E, respectively. When assembling the automatic transmission 100, the intermediate transmission shaft 1
4 is fitted into the center support 158, but prior to that, the shell type needle roller bearing 1 is fitted onto the outer peripheral side of the intermediate transmission shaft 14 and assembled. The shell-type needle roller bearing 1 has a structure as shown in FIG. A tapered surface 2C is formed on the inner diameter side of the return portion 2A. The shape of the taper 2C is adjusted according to the outer diameter of the seal rings 7F, 7G, and 7H so that the tapered surface 2C comes into contact with the outer circumference of the seal ring when the shell-type needle roller bearing 1 is assembled. It is determined appropriately. Reference numeral 3 designates a plurality of needle rollers which rotatably support the intermediate transmission shaft 14 attached to the inside of the shell 2, and whose support surfaces are formed to have a smaller diameter than the tip of the bent portion, and which have both ends 4A and 3. 4B are bent portions 2A and 2 at both ends of the shell 2, respectively.
A cylindrical gauge 4 fixed to the inner surface of B is loosely fitted into a plurality of windows, which are openings. Further, the tapered surface 2C is formed such that its extension line does not intersect the outer peripheral surface of the needle roller 3. When the shell type needle roller bearing 1 having this configuration is inserted onto the outer circumferential side of the intermediate transmission shaft 14, the seal rings 7F, 7G, 7H are
Each oil seal groove 7 is pressed by the tapered surface 2C of the shell type needle roller bearing 1.
Because it is pushed smoothly into C, 7D, and 7E,
The shell type needle roller bearing 1 can be fitted smoothly, and each seal ring 7F, 7
Damage to the surfaces of G and 7H is prevented. In this embodiment, the other bent portion 2B has a curled shape, and this shape facilitates the work of removing the shell-type needle roller bearing 1. Here, although there is no problem in attaching and detaching the shell type needle roller bearing 1 even if the bent portions 2A and 2B have a curled shape, it is preferable that the bent portions 2A and 2B have the above-mentioned tapered surfaces. In other words, a straight tapered surface in contact with the seal ring allows the shell-type needle roller bearing 1 to be installed and removed more smoothly than a curled shape, and it also requires bending, which increases costs. It is. The output shaft 36 is formed into a flange plate which is thinned by a cutting process in order to form a curled portion, and then bent and meshes with the ring gear R2 of the third planetary gear set p3 at the intermediate portion 37 and has a sleeve 81 that protrudes rearward. 82 and is spline fitted, rear 3
At 8, it is spline fitted to the sleeve yoke. In the overdrive mechanism chamber 133, a first planetary gear set p is provided on the rear side of the input shaft 11.
1 is provided, the ring gear R0 is connected to the intermediate transmission shaft 14 via a flange plate 22, and the planetary carrier P0 is connected to the flange portion 12 of the input shaft 11.
a, and the sun gear S0 is connected to the inner race shaft 2.
It is formed in 3. On the front side of the first planetary gear set p1, a first hydraulic servo drum 24 that opens rearward is fixed to an inner race shaft 23, and an annular piston 25 is fitted between the outer peripheral wall of the drum and the inner race shaft 23, and the clutch C0 A return spring 26 is attached to the inner race shaft 23 side, and a clutch C0 is attached to the inner side of the outer peripheral wall, and is connected to a planetary carrier P0 via the clutch C0. A one-way clutch F0 having the inner race shaft 23 as an inner race is provided on the inner periphery of the first hydraulic servo drum 24, and a clutch C0 and a brake B0 are provided on the outer periphery between the outer race 27 and the transmission case 130. Rear intermediate support wall 15
A piston 29 is fitted into the front side of the outer cylindrical part 31 of 9 to form a hydraulic servo B-0 of the brake B0, and a return spring 32 is fitted into the tip of the outer cylindrical part 31. Inside the underdrive mechanism chamber 134, at the front, a second hydraulic servo drum 41 that opens rearward is rotatably fitted onto the center support 158, and an annular piston 42 is fitted between its inner and outer circumferential walls to drive the clutch C2. A hydraulic servo C-2 is formed and a return spring 4 is installed on the inner peripheral wall side.
4. Clutch C2 is attached to the inside of the outer wall. On the rear side of the second hydraulic servo drum 41,
A third hydraulic servo drum 46 that is open at the rear and has a clutch hub 35 welded to the front is fixed to the rear end 15 of the intermediate transmission shaft 14, and an annular piston 47 is fitted between the rear end 15 and the outer peripheral wall. to form a hydraulic servo C-1 of the clutch C1, a return spring 49 is attached to the inner circumference, and a clutch C2 is attached to the outer circumference of the clutch hub 35.
Second hydraulic servo drum 4 via clutch C2
1 and a third hydraulic servo drum 46 are connected. A second planetary gear set p2 is provided on the rear side of the third hydraulic servo drum 46,
The ring gear R1 is connected to the third hydraulic servo drum 46 via the clutch hub 48 and the clutch C1, the planetary carrier P1 is spline-fitted to the tip of the output shaft 36, and the sun gear S1
is formed integrally with the sun gear shaft 45. In addition, a connecting drum 60, which is formed to cover the second and third hydraulic servo drums 41 and 46 and the second planetary gear set p2 in a minimum space, is attached to the outer periphery of the second hydraulic servo drum 41 at its tip. The rear end is connected to the sun gear shaft 45 behind the second planetary gear set p2, and a belt brake B1 is provided on the outer circumferential side. The spline 75 formed inside the transmission case 130 on the rear side of the brake B2 has a spline 75 formed on the inside of the transmission case 130 on the rear side of the brake B2.
2. The outer spline of the fourth hydraulic servo drum 72 and the brake disc b3 of the brake B3 are spline-fitted, and the piston is inserted into the annular hole between the outer circumferential side of the rear support 156 of the rear support wall 157 and the transmission case 130. 77 is fitted to form a hydraulic servo B-3 of the brake B3, and a return spring 79 of the hydraulic servo B-3 is supported by a flange plate attached to the tip of the rear support 156. The brake B
A one-way clutch F1 having the sun gear shaft 45 as an inner race is provided on the inside of the clutch F1, and an outer race 39 is connected to the brake B2. 72 and a one-way clutch F2 spline-fitted on the inner diameter. In the third planetary gear set p3, the sun gear S2 is formed integrally with the sun gear shaft 45, the planetary gear P2 is connected to the outer race 86 of the one-way clutch F2 on the front side, and is also connected to the brake B3, and the parking gear 85 is attached to the outer periphery. A ring gear R2 surrounding the output shaft 36 is connected to the intermediate portion 37 of the output shaft 36. When the shift lever of the automatic transmission is selected to the parking (P) position, the parking claw 84 engages with the parking gear 85 to fix the output shaft 36. 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 in an oil pan 401 fastened to the lower part of the transmission case 130 with bolts 402. 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 the corresponding clutch, brake, and engagement of the clutch in one direction. (L) indicates that the corresponding one-way clutch is engaged only in engine drive conditions and not in engine brake conditions. Furthermore, although L is engaged in the corresponding one-way clutch engine drive state, this engagement is not necessarily required since power transmission is guaranteed by a clutch or brake built in parallel. Indicates that (lock). Further f
indicates that the corresponding one-way clutch is free. Additionally, an x indicates that the corresponding clutch and brake are released.

[Brief explanation of the drawing]

FIG. 1 is a cross-sectional view showing an embodiment of a shell-type needle roller bearing disposed in an automatic transmission for a vehicle according to the present invention, FIG. 2 is a cross-sectional view of the automatic transmission according to the present invention, and FIG. It is an enlarged view of the main part in FIG. 2. 1...Shell type needle roller bearing, 2
... Cylindrical shell, 2A, 2B ... Bending part,
2C...Tapered surface, 100...Automatic transmission.

Claims (1)

[Claims] 1. A rotating shaft, a seal ring disposed in a groove cut in the rotating shaft, a fixing member that supports the rotating shaft on the inner diameter side, and a seal ring disposed on the inner diameter side of the fixing member. a shell-type needle roller bearing that is installed to relatively rotatably support the rotating shaft and that is assembled over the seal ring; the shell-type needle roller bearing has a cylindrical shell that is fixed to the inner diameter side of the fixed member; a bent portion formed at both ends of the cylindrical shell; a gauge having a plurality of openings with both ends locked to the bent portion; and a gauge rotatably fitted into the opening of the gauge. a roller which rotatably supports the rotating shaft and whose support surface is formed to have a smaller diameter than the tip of the bent portion, on the inner diameter side of the at least one bent portion;
An automatic transmission for a vehicle, characterized in that a tapered surface is formed so as to be brought into contact with the outer circumferential portion of the seal ring during assembly so that the extension line does not intersect with the outer circumferential surface of the roller.