JPH071540Y2 - Output shaft support structure for automatic transaxle - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION (a) Field of Industrial Application The present invention relates to an output shaft support structure for an automatic transaxle.

(B) Conventional technology As an output shaft supporting structure of a conventional automatic transaxle, for example, "Automatic transaxle RN
4F02A type, RL4F02A type, 1984 maintenance manual "(issued by Nissan Motor Co., Ltd.) In the automatic transaxle shown in this figure, a counter shaft is arranged parallel to the output shaft of the automatic transmission mechanism.The output shaft and the counter shaft are connected by the output gear and the counter gear, and the counter shaft is connected to the differential mechanism. Be connected. The output shaft and the output gear are integrally formed, and the output shaft is supported by two taper roller bearings.

(C) Problems to be Solved by the Invention However, in the above-mentioned conventional example, the friction loss of the taper roller bearing is large and the transmission efficiency is deteriorated, and the taper roller bearing arranged on the end side of the output shaft is Since the output gear is located in the concave part on the inner diameter side (this is to reduce the axial dimension), the rigidity of the output gear is low and the gear noise of the output gear is large. There is a point.

The present invention aims to solve the above problems.

(D) Means for Solving the Problems The present invention solves the above problems by supporting the output shaft by a ball bearing, a radial needle bearing and a thrust needle bearing. That is, in the output shaft supporting structure of the automatic transaxle according to the present invention, the output shaft (30) is
The radial bearing supported by the ball bearing (56) provided on the side cover (52) attached to the casing (0) and the inner diameter of the hollow output retainer (60) fixed to the casing body by a plurality of bolts (58). Radially supported by the needle bearing (62),
A side surface of the output gear (32) opposite to the ball bearing is axially supported by a thrust needle bearing (64) supported by the casing body, and the thrust needle bearing has a diameter equal to that of the bolt for fixing the output retainer. It is arranged on the outer peripheral side. The reference numerals in parentheses indicate the corresponding members in the embodiments described later.

(E) Action The radial load is supported by the ball bearing and the radial needle bearing. The thrust load acting on the output shaft when the engine is driven is supported by the thrust needle bearing. A slight reverse thrust load during engine braking is supported by the ball bearings. The thrust needle bearing has a large diameter arranged on the outer peripheral side of the bolt and has a sufficient load capacity. In addition, the position of the output gear near the outer diameter part (that is,
Since the position close to the tooth surface is supported, the deformation of the output gear is reduced and the gear noise is reduced. Since the thrust needle bearing and the bolt are arranged so as not to overlap each other in the axial direction, the axial dimension is also small.

(F) Example FIG. 2 shows a frame diagram of an automatic transaxle. The automatic transmission mechanism portion of an automatic transaxle connected to an engine 10 mounted laterally with respect to a vehicle, that is, orthogonal to the vehicle front-rear direction, includes a torque converter 12, a planetary gear transmission mechanism 14, and the like. The torque converter 12 to which the rotation from the engine 10 is input has a pump impeller 18, a turbine runner 20, and a stator 22.
And a lockup clutch 24. The turbine runner 20 is connected to the input shaft 26, and when the lockup clutch 24 is released, the rotational force is transmitted from the pump impeller 18 to the input shaft 26 via fluid, and the lockup clutch 24 is engaged. Then, the rotational force is mechanically input to the input shaft 26. The lockup clutch 24 operates by the differential pressure between the apply chamber T / A and the release chamber T / R. In addition,
The torque converter 12 is configured to drive the oil pump 28. The planetary gear speed change mechanism 14 is the first planetary gear set.
G ₁ and has the second has a planetary gear set G _2, the first planetary gear set
G ₁ is the first sun gear S ₁ , the first internal gear R ₁ ,
A first pinion carrier PC ₁ supporting a first pinion gear P ₁ that meshes with both gears S ₁ and R ₁ at the same time, and a second planetary gear set G ₂ includes a second sun gear S ₂ and a second sun gear S ₂ . Two
A second pinion carrier that supports an internal gear R ₂ and a second pinion gear P ₂ that meshes with both gears S ₂ and R ₂ at the same time.
It consists of PC ₂ and. The first sun gear S ₁ has an input shaft 26
Always connected to the 1st pinion carrier PC ₁
The second internal gear R ₂ is always connected to the output shaft 30. The first internal gear R ₁ is connected to the second pinion carrier via the forward one-way clutch F / O and the forward clutch F / C arranged in series, and the over-rank clutch O / C arranged in parallel therewith. PC ₂
Can be connected with. The second sun gear S ₂ is a reverse clutch
The input shaft 26 can be connected via the R / C, and the second pinion carrier PC ₂ can be connected to the input shaft 26 via the high clutch H / C. Second Sun Gear S ₂ is a band brake B / B
The second pinion carrier PC ₂ can be fixed to the stationary part by means of the low one-way clutch L / O and the low and reverse brake L & R / B which are arranged in parallel with each other.
It can be fixed to the stationary part via and. An output gear 32 is provided integrally with the output shaft 30. A counter gear 34 is provided so as to mesh with the output gear 32, and a reduction gear 36 is connected to the counter gear 34 via a counter shaft 35 so as to rotate integrally. The reduction gear 36 meshes with the ring gear 38 of the differential mechanism 16. The drive shafts 40 and 42 project left and right from the differential mechanism 16, and the left and right front wheels are connected thereto.

This planetary gear speed change mechanism 14 operates clutches F / C, H / C, O / C and R / C, brakes B / B and L & R / B, and one-way clutch F / O and L / O in various combinations. Each element of the planetary gear set G ₁ and G ₂ (S ₁ , S ₂ , R ₁ , R ₂ , PC ₁
And it can change the rotating state of the PC _2), whereby it is possible to change various rotational speed of the output shaft 30 to the input shaft 26. That is, by operating each clutch, brake, etc. in a combination as shown in FIG. 3, it is possible to obtain the fourth forward speed and the first reverse speed. In addition, ○ in FIG.
The mark indicates that the clutch and brake are engaged,
Also, in the case of a one-way clutch, the engaged state is shown. In addition, 2A, 3R and 4A are shown in the band brake B / B column respectively for the second speed apply chamber 2A, the third speed release chamber 3R and the fourth speed apply of the hydraulic servo device that operates the band brake B / B. The chamber 4A is shown, and the mark ○ indicates that hydraulic pressure is being supplied. Further, α ₁ and α ₂ are the ratios of the number of teeth of the sun gears S ₁ and S _{2 to} the number of teeth of the internal gears R ₁ and R ₂ , respectively, and the gear ratio is the ratio of the input shaft 26 to the rotation speed of the output shaft 30. It is the ratio of the number of rotations.

By the operation of the planetary gear speed change mechanism 14 as described above, the input shaft
The rotation of 26 is subjected to a predetermined speed change and is output to the output shaft 30. The rotational force of the output shaft 30 is transmitted to the ring gear 38 of the differential mechanism 16 via the output gear 32, the counter gear 34, and the reduction gear 36. As a result, the left and right front wheels can be driven via the drive shafts 40 and 42. By doing so, it is possible to perform automatic forward four-speed shift with overdrive.

A part of the power transmission mechanism shown as a frame diagram in FIG.
The figure shows the actual structure. In FIG. 1, members corresponding to those shown in FIG. 2 are designated by the same reference numerals. A side cover 52 is attached to the casing body 50 with bolts 54. The left end side in FIG. 1 of the output shaft 30 integrally provided with the output gear 32 is supported by the side cover 52 via a ball bearing 56. Casing body
Output retainer with bolt 58 on the inside of 50
60 is installed and this output retainer 60
A radial needle bearing 62 is provided on the inner diameter of the output shaft 30 to support the right end side of the output shaft 30 in the figure. Further, a thrust needle bearing 64 is arranged between the wall portion 51 of the casing body 50 and the side surface of the output gear 32. The thrust needle bearing 64 is arranged on the outer peripheral side of the arrangement diameter of the bolt 58. Pistons 66 and 68 of the overrunning clutch O / C and the forward clutch F / C are provided on the outer peripheral side of the output retainer 60, respectively.
A clutch drum 70 for accommodating is disposed.

Next, the operation of this embodiment will be described. The rotational force input from the engine 10 to the torque converter 12 is output from the automatic transmission mechanism to the output shaft 30, transmitted to the counter shaft 35 via the output gear 32 and the counter gear 34, and further transmitted to the differential mechanism 16. To be done. During the power transmission, a radial force (radial load) and an axial force (thrust load) act on the output shaft 30 due to the engagement of the output gear 32 and the counter gear 34. Most of the radial force acting on the output shaft 30 is supported by ball bearings 56. The remainder of the radial force is supported by radial needle bearing 62. On the other hand, the axial force acting on the output shaft 30 is supported by the thrust needle bearing 64. The thrust needle bearing 64 is arranged on the side that supports the thrust force that acts when the engine is driven. It should be noted that the thrust force in the opposite direction acts also during engine braking, but this is a relatively small value and can be supported by the ball bearing 56.

Thrust needle bearing 64 with relatively large axial force
Since the output gear 32 is supported by, the amount of deformation of the output gear 32 is reduced, which reduces gear noise. Also,
Since the thrust needle bearing 64 is arranged on the outer peripheral side of the bolt 58, the axial dimension is also reduced as compared with the case where it is disposed at the same position as the bolt 58, and the axial dimension of the entire automatic transaxle can be reduced. . Further, the friction loss of the ball bearing 56, the radial needle bearing 62, and the thrust needle bearing 64 is smaller than that in the case of using the tapered roller bearing, so that the transmission efficiency can be improved.

(G) Effect of the Invention As described above, according to the present invention, the output shaft is supported by the ball bearing, the radial needle bearing and the large diameter thrust needle bearing, so that the transmission efficiency can be improved. At the same time, the deformation of the output gear can be reduced to reduce gear noise, and the axial dimension can be reduced.

[Brief description of drawings]

FIG. 1 is a diagram showing an embodiment of the present invention, FIG. 2 is a skeleton diagram of an automatic transaxle, and FIG. 3 is a diagram showing a combination of elements that act at each shift speed. 30 …… Output shaft, 32 …… Output gear, 34 …… Counter gear,
50 …… Casing body, 52 …… Side cover, 56 …… Ball bearing, 58 …… Bolt, 60 …… Output retainer, 62 …… Radial needle bearing, 64 …… Thrust needle bearing.

Claims (1)

[Scope of utility model registration request] 1. An output shaft of an automatic transmission mechanism and a counter shaft parallel thereto are connected by an output gear and a counter gear provided so as to rotate integrally with the output shaft and the counter shaft, respectively. Is a support structure for the output shaft of an automatic transaxle, which is connected to a differential mechanism so that torque can be transmitted.The output shaft consists of a ball bearing provided on a side cover attached to the casing body and a plurality of bolts on the casing body. It is supported radially by a radial needle bearing supported by the inner diameter of a fixed hollow output retainer, and the side of the output gear opposite to the ball bearing is thrust by a thrust needle bearing supported by the casing body. The thrust needle bearing is An output shaft support structure for an automatic transaxle, wherein the output shaft support structure is arranged on the outer peripheral side of the arrangement diameter of the bolt for fixing the putt retainer.