JPS6179069A - Bearing support sleeve for transmission of vehicle - Google Patents

Abstract

PURPOSE:To enlarge the size of a bearing, by embedding a bearing support sleeve at the time of casting, so as to secure the sleeve to a support member. CONSTITUTION:A ball bearing 101 is made of an iron having a lower coefficient of thermal expansion than a fixed member 157, and includes balls 101A and an outer race 101B. When the fixed member 157 is cast, an already molded sleeve 156A, which has the same coefficient of thermal expansion as the outer race 101B, is put in a mold in order to prevent the position of the outer are race from deviating due to the thermal expansion of the fixed member. According to this constitution, the thickness of the portion of the fixed member, on which the sleeve is secured, can be reduced to enlarge the size of the bearing.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to a sleeve that supports an outer race of a rolling bearing that facilitates the rotation of a rotating body within a vehicle transmission.

[Prior Art] Conventionally, for example, a rotating body (output gear) 6 that rotates in response to power transmission as shown in FIG. 4, a fixed member 157 that supports the rotating body 6, and the rotating body 6 and the fixed member 151, a rolling member 101A is arranged between the rotating member 151 to smoothly rotate the rotating body 6;
Rolling bearing (ball bearing) 101 with C
The outer race 101B of the rolling bearing 101 of the vehicle transmission has a structure similar to the outer race 101B between the fixing member 157 and the outer race 101B to prevent displacement of the outer race 101B due to thermal expansion of the fixing member. Sleeve 156A with coefficient of thermal expansion
was installed by press-fitting.

[Problems to be Solved by the Invention] In the above-mentioned conventional technology, the sleeve is fixed to the fixing member by a press-fitting process, so the sleeve mounting position of the fixing member is fixed in order to maintain the configuration to prevent deformation due to the press-fitting of the sleeve. wall thickness is required. Therefore, when increasing the size of a rolling bearing for the purpose of increasing capacity, it is necessary to increase the outside diameter of the fixed member and change the shape of each part of the transmission installed on the fixed member. It was difficult to increase capacity.

An object of the present invention is to eliminate the step of press-fitting the sleeve into the fixing member by inserting the sleeve into a mold and casting the fixing member, thereby making it possible to form the fixing member thin in the area where the sleeve is fixed. Another object of the present invention is to provide a vehicle transmission in which the size of the rolling bearing can be increased by making the identification member thinner, and the capacity of the rolling bearing can be increased.

[Means for Solving the Problems] In order to solve the above problems, a bearing support sleeve for a vehicle transmission according to the present invention includes a rotating body that rotates in response to power transmission, and the rotating body formed by casting. a supporting member;
a bearing disposed between the rotating body and the support member; and a sleeve disposed between the support member and the bearing to prevent displacement of the bearing due to a difference in thermal expansion between the support member and the bearing. In the vehicle transmission, the sleeve is fixed to the support member by casting.

[Operation and Effects of the Invention 1] The bearing support sleeve of the vehicle transmission of the present invention having the above-mentioned configuration is obtained by inserting the sleeve into a mold and casting the fixing member, thereby reducing the wall thickness of the fixing member at the portion where the sleeve is fixed. Since the thickness of the bearing can be made thinner, the size of the rolling bearing can be increased, and the torque transmission capacity of the transmission can be increased.

[Example] Next, a bearing support sleeve for a vehicle transmission according to the present invention will be described based on an example shown in the drawings.

FIG. 2 does not show a sectional view of a front engine front drive (FF) type automatic transmission with four forward speeds and one reverse speed to which an embodiment of the bearing support sleeve for a vehicle transmission of the present invention is applied.

The automatic transmission 11100 is a hydraulic torque converter 200
, a transmission 300, a differential 90, and a hydraulic control device (not shown).

The transmission 300 includes a first planetary gear set 40, a second planetary gear set 50, and two multi-disc clutches C1, C2, 1 operated by a hydraulic sanibo.
Two band brakes B1. Two multi-disc brakes B2, B
3, one one-way latch F1, one one-way brake F2, an underdrive device 10 with three forward stages and one reverse stage, a third planetary gear set 80, and one multi-stage gear set 80 operated by a hydraulic servo. The sub-transmission device 60 includes a plate clutch C3, one multi-plate brake B4, and one one-way brake F3.

The housing 110 of the automatic transmission includes a front housing 120, a torque converter 200 formed integrally with each chamber housing the differential 90, an underdrive device 10, each chamber housing the auxiliary transmission 60, and the differential 90. Main housing 130 integrally formed with rear cover 131 and underdrive device 1
The output gear 6 and the input gear 7 of the auxiliary transmission 60, which are rotating bodies according to the present invention, rotate upon receiving power transmitted from the first intermediate transmission shaft 4.
It consists of a rear cover 140 that houses the automatic transmission and covers the rear side of the automatic transmission, a front housing 120,
Main housing 1301 Main housing 130 and rear cover 140 are each firmly fastened with bolts.

Torque converter 200 is housed in a torque converter chamber 121 that is open at the front (engine side). Between the cylindrical underdrive chamber 132 continuous to the rear of the torque converter chamber 121 and the torque converter chamber 121, there is a cylindrical portion 152 which is an annular plate body that houses an oil pump 150 therein and protrudes forward inward. An oil pump front cover 151 is firmly fastened to the main housing 130, and a cylindrical front support that is coaxial with the cylindrical portion 152 and protrudes rearward is provided on the rear side of the oil pump front cover 151. An oil pump cover 154 having a diameter of 153 is tightened, and the oil pump front cover 151 and the oil pump cover 154 are connected to the partition wall 15 of both chambers.
5 is formed. Further, at the rear of the underdrive chamber 132, a cylindrical center support 15 that protrudes forward is provided.
A fixing member 151 made of aluminum alloy is provided to support the output gear 6 according to the present invention. An underdrive chamber 132 is formed between the partition wall 155 and the fixed member 157, an output gear chamber 141 of the transmission is formed between the fixed member 157 and the rear cover 140, and the rear cover 140 has the front support 1
A cylindrical rear support 142 coaxial with 53 projects forward.

A cylindrical auxiliary transmission chamber 133 is provided in parallel to the side of the cylindrical underdrive chamber 132, and a hole-shaped front support 158 is provided in the wall 123 of the front housing 120 at the front center of the auxiliary transmission chamber 133. is provided, and at the rear,
A fixing member 160 is provided to which a cylindrical center-length boat 159 that protrudes forward and is fastened with bolts is provided, and an input gear chamber 142A of the sub-transmission device 60 is formed between the rear cover 140 and the fixing member 160. The space between this and the wall 123 forms an ill transmission chamber 133.
A fixed shaft 203 of a one-sided clutch 202 that supports the stator 201 of the torque converter 200 is fitted inside the I front support 153, and an input shaft 1 of the transmission, which is the output shaft of the torque converter 200, is fitted inside the fixed shaft 203. is rotatably supported. The input shaft 1 has a large diameter rear end 2 that projects rearward from the front support 153, and a rearward hole 3 is formed in the center of the rear end 2.

A first intermediate power transmission shaft 4 arranged in series with the input shaft 1 is rotatably mounted behind the input shaft 1, and the first intermediate power transmission shaft 4 has its tip slidably in contact with the hole 3; As shown in FIG.
The cylindrical portion 6A of the output gear 6 is spline-fitted into the inner hole 6B of the output gear 6, and the rotating body is connected between the center support 156 and rear support 142 of the fixed member 151 and the cylindrical portion 6A of the output gear 6. A ball bearing 101 is a rolling bearing that allows a certain output gear 6 to rotate smoothly.
．． 102, the ball bearing 101 is made of iron having a smaller coefficient of thermal expansion than the fixed member 157 made of aluminum alloy, and has a ball 101A1 which is a rolling member, an outer race 101B and an inner race 101C, The outer race 101 is formed on the inner circumferential side of the center support 156 of the fixing member 151 at the outer circumferential position due to thermal expansion of the fixing member 157.
In order to prevent displacement of the outer race 101B, a sleeve 156A having the same coefficient of thermal expansion as the outer race 101B is attached to the fixing member 157.
Sleeve 156A already formed in the mold during casting
is inserted, molded and installed, and the ball bearing 10
1 is larger in size than conventional rolling bearings. In addition, the sleeve 156A eliminates the press-fitting process for fixing it to the center support 156, and the sleeve 156A
Since the mounting surface of the center support 156 of 6A can be machined by rough finishing, production costs can be kept low, and the center support 156 has high rigidity because the sleeve 156A is fixed by casting. A sun gear shaft 5 is rotatably fitted on the outer side of the first intermediate transmission shaft 4 on the front end side via a bearing.

Input gear 7 of sub-transmission device 60 meshing with output gear 6
The cylindrical portion 7A at the center is supported by the center support 1-159 via the roller bearing 103, and the rear end portion of the second intermediate transmission shaft 8 passing through the center of the sub-transmission chamber 133 is inserted into the inner hole IB. are spline fitted. The second intermediate power transmission shaft 8 has a flange-shaped projection 81 at the intermediate portion on the front end side.
It has a rod shape with an oil passage 8A formed inside thereof, and its tip is supported by the hole-shaped front support 158 via a roller bearing 104. A pair of roller bearings 104 on the second intermediate transmission shaft 8 and a 7-lung-shaped protrusion 81 are assembled with a spring material 105 sandwiched between them and preloaded with a nut 82 tightened at the tip. The two-shaft automatic transmission (underdrive device 10 and sub-transmission device 60
A transmission shaft 9 is supported, which is an output section forming an output gear 92 of a multi-stage transmission (multi-stage transmission), and the output gear 92 of the transmission shaft 9 meshes with a large drive gear 91 of a differential 90.

Further, a seven-lung-shaped projection 81 on the second intermediate transmission shaft 8
A cylindrical sun gear @6 is located between the center support 159 and the center support 159.
1 is rotatably supported via a bushing, and a cylindrical inner race shaft 62 is rotatably supported via a bushing on the outside of the center support 159.
The outer side of the rear end and the inner side of the tip of the inner race shaft 62 are spline-fitted.

In the underdrive chamber 132, at the front, a first hydraulic servo drum 11 that opens rearward is rotatably fitted onto a front support 153, and an annular piston 12 is fitted between the inner and outer circumferential walls of the first hydraulic servo drum 11 to operate the clutch C2. A hydraulic servo C-2 is formed, and a return spring 14 is attached to the inner circumferential wall, and a clutch C2 is attached to the inner side of the outer circumferential wall. On the rear side of the first hydraulic servo drum 11, there is a second hydraulic servo drum 11 which is open to the rear and has an annular projection 15 at the front.
A hydraulic servo drum 16 is fixed to the rear end portion 2 of the input shaft 1, and an annular piston 17 is fitted between the rear end portion 2 and the outer peripheral wall to form the hydraulic servo C-1 of the clutch C1. A return spring 19 is installed on the side, a clutch C1 is installed inside the outer peripheral wall, and an annular projection 15 is installed on the side.
A clutch C2 is attached to the outer periphery of the hydraulic servo drum 11.16, and the first and second hydraulic servo drums 11.16 are connected via the clutch C2. A first planetary gear set 40 is provided on the rear side of the second hydraulic nervo drum 16, and its ring gear R1
is connected to the second hydraulic servo drum 16 via a clutch C1, the carrier P1 is spline-fitted to the tip of the first intermediate transmission shaft 4, and the sun gear S1 is integrated with the sun gear shaft 5. In addition, the first and second hydraulic servo drums 11
．． 16 and the first planetary gear set 40 in a minimum space, the connecting drum 20 is fixed at its tip to the outside of the first hydraulic servo drum 11, and its rear end is attached to the rear of the first planetary gear set 40. It is connected to the sun gear shaft 5 on the side, and a band brake B1 is provided on the outer circumferential side.

An annular third hydraulic servo drum 22 opening rearward is fixed in the surplus space 21 outside the connecting drum outside the first planetary gear sets 1 to 40, and a piston 23 is fitted into the surplus space 21 outside the connecting drum of the brake B2. form. A spline groove 25 formed inside the main housing 130 on the rear side of the hydraulic servo B-2 is provided with a brake B-2 from the front.
2. The outer race 26 of the one-way brake F2 and the multi-plate brake B3 are installed in this order, and the fixing member 157 on the rear side
Center support 156 outer circumferential side and torque converter 20
The piston 27 is fitted into the annular hole between the center support 1 and the hydraulic servo B-3 of the multi-disc brake B3.
56 is supported by a 7 lunge plate 30 attached to the tip.

A one-way latch i:1 for inner racing the sun gear shaft 5 is arranged inside the multi-disc brake B2, an outer race 31 is connected to the multi-disc brake B2, and a one-way latch i:1 is provided on the rear side of the one-way clutch F1. 2nd planetary gear set 5
0 is attached. The second planetary gear set 50
, the sun gear S2 is integrally formed with the sun gear shaft 5, the carrier P2 is connected to the inner race 32 of the outer one-way brake F2, and is also connected to the multi-plate brake B3, and the sun gear R2 is connected to the first intermediate transmission shaft 4. is connected to.

A third planetary gear set 80 is provided on the rear side of the transmission shaft 9, and its ring gear R3 is connected to the projection 8 of the second intermediate transmission shaft 8.
1 via a flange plate 63, and the carrier P3 has a side wall 6 provided with an annular projection 69 connected to the clutch C3.
4a and one end of the side wall 64a is a rounded part 64b, and a cylindrical part 64c extends from the rounded part 64b of the side wall 64a.
A connection f, which is an input section, is connected via an output drum 64 consisting of
5111, and the sun gear S3 is formed on the sun gear shaft 61. On the rear side of the third planetary gear set 80, a forward-opening fourth hydraulic servo drum 65 is fixed to the inner race shaft 62, and an annular piston 66 is fitted between the outer circumferential wall and the inner race shaft 62 to provide a clutch. In addition to forming a hydraulic servo C-3 of C3, a return spring 68 is attached to the inner race shaft 62 side, and a clutch C3 is attached to the inside of the outer peripheral wall, and is connected to the carrier P3 via the clutch C3. A one-way brake F3 with the inner race shaft θ2 as an inner race is provided on the rear side of the fourth hydraulic servo drum 65, a brake B4 is provided on the rear side between the inner race shaft 62 and the main housing 130, and a brake B4 is provided on the rear side between the inner race shaft 62 and the main housing 130. The piston 70 is fitted into the annular projection 69 between the outer peripheral side of the center support 159 of the fixed member 160 and the main housing 130, and the brake B
4 hydraulic servos B-4 are formed, and return springs 72 are fitted into grooves provided at equal intervals on the outer circumferential side of the brake B4.

A differential gear chamber 12 is provided on the side of the torque converter chamber 121.
2, a differential 90 is supported by a tapered roller bearing 107, and a large driving gear 91 provided at the rear end meshes with the output gear 92.

The transmission 300 engages each clutch and brake using hydraulic pressure selectively output from a hydraulic pressure unit (not shown) to the hydraulic servo of each frictional engagement device according to vehicle running conditions such as vehicle speed and throttle opening. Alternatively, the transmission is released, and the gear is shifted to four forward gears or one reverse gear.

Table 1 shows examples of the gear positions (RANGE) achieved by the operation of each clutch, brake, one-way clutch, and one-way brake.

Table 1 In Table 1, O indicates that the corresponding clutch, brake, one-way clutch, or one-way brake is engaged. However, Δ indicates that the corresponding one-sided clutch or one-sided brake is engaged only in the engine drive state, and is not engaged in the engine brake state. Roughly ◎ means that the corresponding one-sided clutch or one-sided brake is engaged in the engine drive state, but this engagement is because the transmission of power is guaranteed by the clutch or brake built in parallel. Indicates that it is not necessarily required.

FIG. 3 shows another embodiment of the invention.

This example shows center support 15G of sleeve 156A.
By providing flanges 156B and 156C at both ends of the side where the sleeve 156A and the center support 156 are cast, it is possible to improve the strength of the center support 156 and to further prevent misalignment of the sleeve 156A and the center support 156.

[Brief explanation of the drawing]

FIG. 1 is a cross-sectional view showing a bearing support sleeve for a vehicle transmission according to the present invention, FIG. 2 is a cross-sectional view of an automatic transmission incorporating the bearing support sleeve for a vehicle transmission shown in FIG. 1, and FIG. The figure is a sectional view showing another embodiment of the present invention, and FIG. 4 is a sectional view of a conventional bearing support sleeve of a vehicle transmission.

Claims (1)

[Scope of Claims] 1) A rotating body that rotates in response to power transmission, a supporting member for the rotating body formed by casting, and a bearing disposed between the rotating body and the supporting member, A vehicular transmission comprising: a sleeve disposed between the support member and the bearing to prevent displacement of the bearing due to a difference in thermal expansion between the support member and the bearing; A bearing support sleeve for a vehicle transmission, characterized by being fixed by casting. 2) The bearing support sleeve for a vehicle transmission according to claim 1, wherein the fixing member is a cylindrical support portion of a transmission case. 3) The bearing support sleeve for a vehicle transmission according to claim 1, wherein the sleeve is provided with flanges at both ends of the side to be cast into the support member.