JP3122202B2 - Reduction gear support structure for transmission - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a reduction gear supporting structure for transmitting the rotation of an output shaft of a transmission at a reduced speed.

[0002]

2. Description of the Related Art A transmission configured to transmit the output of an engine obtained through a fluid coupling to wheels at a predetermined speed ratio has been disclosed in, for example, Japanese Patent Application Laid-Open No. 1-112076. Such a belt-type continuously variable transmission is known. This continuously variable transmission has a transmission mechanism in which a belt is suspended between a primary pulley and a secondary pulley spaced apart from the primary pulley.

In such a continuously variable transmission, due to its structure,
When transmitting the output of the transmission to the wheels, deceleration with a large reduction ratio is required. Therefore, a reduction gear is provided between the output shaft of the transmission and the differential. Further, as is apparent from FIG. 1 of the above publication, the transmission is housed in a casing composed of a transmission mechanism housing and a coupling housing fixed to face each other, and one end of a shaft of the reduction gear. Is rotatably supported by the transmission mechanism housing via a bearing, and the other end of the shaft is rotatably supported by the fluid coupling housing via a bearing. The transmission mechanism housing and the fluid coupling housing are generally positioned with respect to each other with reference to a knock pin, and the bearings supporting both ends of the shaft of the reduction gear are aligned by this positioning.

[0004]

However, in the above-mentioned conventional structure for supporting the reduction gear, two ends for supporting both ends of the shaft of the reduction gear due to a dimensional error between the transmission mechanism housing and the joint housing. There is a problem that a misalignment occurs between the bearings, which causes the shaft of the reduction gear to vibrate and generate gear noise.

In view of the above problems, an object of the present invention is to provide a reduction gear supporting structure capable of accurately aligning two bearings that support both ends of a shaft of a reduction gear.

[0006]

Reduction gear supporting structure of the transmission according to the present invention the means for solving problem] includes a bearing cover provided speed change mechanism housing separately from, set in the bearing cover
And supports one end of the reduction gear shaft that supports the reduction gear
And a bearing for the upper SL bearing cover is, with respect to the joint housing for supporting the other end portion of the reduction gear shaft, is positioned by a coaxial fitting means formed between the bearing cover and the joint housing It is characterized by being attached.

The coaxial fitting means comprises a soldering fitting portion formed on the bearing cover and the joint housing, and the soldering fitting portion is simultaneously formed with each bearing support portion of the bearing cover and the joint housing. It is formed by processing.

[0008]

Reduction gear supporting device for a transmission according to action and effect of the present invention, a bearing cover provided to the variable speed mechanism housing a separate body as described above, provided in the bearing cover
Provided, and a bearing for supporting one end portion of the reduction gear shaft, base <br/> A ring cover, relative to the joint housing for supporting the other end portion of the reduction gear shaft, coaxial fitting as spigot joint fitting By being positioned and attached by the means, as compared with the conventional case, one end of the shaft of the reduction gear is supported by the speed change mechanism housing provided opposite to the joint housing, as in the related art. Accuracy is higher,
Vibration of the shaft of the reduction gear is suppressed, and gear noise generated from the reduction gear can be reduced.

[0009] In particular, since the stamping fitting portion is formed simultaneously with the bearing support portions of the bearing cover and the joint housing, the alignment accuracy becomes extremely high, and the gear noise generated from the reduction gear is reduced. It can be significantly reduced.

[0010]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment in which a reduction gear supporting structure for a transmission according to the present invention is applied to a belt type continuously variable transmission will be described below with reference to the drawings.

FIG. 2 is a skeleton diagram showing the entire configuration of the continuously variable transmission Z. The continuously variable transmission Z is a continuously variable transmission for driving front wheels, and includes a torque converter B connected to an output shaft 1 of an engine A, a forward / reverse switch groove C, a belt transmission mechanism D, and a reduction mechanism. E and a differential mechanism F.

The torque converter B has an engine output shaft 1
The pump impeller 3 fixed to one side of the pump cover 7 and integrally rotated with the engine output shaft 1
And a turbine runner 4 rotatably provided in the space inside the pump cover 7 so as to face the pump impeller 3 and a torque increasing function interposed between the pump impeller 3 and the turbine runner 4. And a stator 5 to be used. The turbine runner 4 is connected via a turbine shaft 2 to a carrier 15 which is an input member of a forward / reverse switching mechanism C described later, and the stator 5 is connected via a one-way clutch 8 and a stator shaft 9 to a transmission case 19. Have been.

Further, a lock-up clutch is arranged between the turbine runner 4 and the pump cover 7. The lock-up clutch includes a piston 6 spline-coupled to the turbine shaft 2 so as to be movable in the axial direction. The piston 6 divides a space in the converter cover 7 into a converter rear chamber 7a on the turbine 5 side and a converter rear chamber 7a. It is divided into a converter front chamber 10 on the cover 7 side. Then, by introducing or discharging the hydraulic pressure into the converter front chamber 10, the pump cover 7 is brought into contact with and integrated with the pump cover 7 according to the pressure difference between the hydraulic pressure in the converter front chamber 10 and the hydraulic pressure in the converter rear chamber 7a. The lock-up state and the converter state separated from the pump cover 7 are selectively realized. In the lock-up state, the engine output shaft 1 and the turbine shaft 2 are directly connected without passing through a fluid. In the converter state, the engine torque is transmitted from the engine output shaft 1 to the turbine shaft 2 via the fluid. .

The forward / reverse switching mechanism C includes a torque converter B
In this embodiment, a forward state in which the rotation of the turbine shaft 2 is transmitted to the belt transmission mechanism D as it is, and a reverse state in which the rotation of the turbine shaft 2 is transmitted to the belt transmission mechanism D in the reverse direction are selectively set. The forward / reverse switching mechanism C is constituted by a double pinion type planetary gear unit. That is, the carrier spline-coupled to the turbine shaft 2
15 includes a first pinion gear 13 that meshes with the sun gear 12;
A second pinion gear 14 meshing with the ring gear 11 is attached. The sun gear 12 is spline-coupled to the primary shaft 22 of the belt drive mechanism D.

Further, a forward clutch 16 for connecting and disconnecting the ring gear 11 and the carrier 15 is provided between the ring gear 11 and the carrier 15, and the ring gear 11 is connected to the transmission case 19 between the ring gear 11 and the transmission case 19. Reverse clutch (or brake) 17 for selective locking
Is interposed.

Therefore, when the forward clutch 16 is engaged and the reverse clutch 17 is released, the ring gear 11 and the carrier 15 are integrated, and the ring gear 11 is rotatable relative to the transmission case 19. Therefore, the rotation of the turbine shaft 2 is output from the sun gear 12 to the primary shaft 22 as the same rotation as it is (forward state).

In contrast, when the forward clutch 16 is released and the reverse clutch 17 is engaged,
Since the ring gear 11 is fixed to the transmission case 19 side and the ring gear 11 and the carrier 15 are relatively rotatable, the rotation of the turbine shaft 2 is reversed via the first pinion gear 13 and the second pinion gear 14. In this state, it is output from the sun gear 12 to the primary shaft 22 (reverse state).

That is, in the forward / reverse switching mechanism C, the forward / backward switching is performed by the selection operation of the forward clutch 16 and the reverse clutch 17.

The belt drive mechanism D is a primary pulley disposed coaxially behind the forward / reverse switching mechanism C.
A belt 20 is suspended between the primary pulley 21 and a secondary pulley 31 spaced apart from the primary pulley 21.

The primary pulley 21 has a fixed conical plate 23 having a predetermined diameter integrally formed with a primary shaft 22 on a primary shaft 22 having one shaft end spline-connected to the sun gear 12 of the forward / reverse switching mechanism C. The movable conical plate 24 is provided so as to be movable in the axial direction of the primary shaft 22. The conical friction surface of the fixed conical plate 23 and the conical friction surface of the movable conical plate 24 form a belt receiving groove 21a having a substantially V-shaped cross section.

On the outer surface 24a side of the movable conical plate 24,
A cylindrical piston 25 is fixed.
Is oil-tightly fitted on the inner peripheral surface of the cylinder 26 fixed to the primary shaft 22 side. The piston 25, the cylinder 26, and the movable conical plate 24 form a single-chamber primary hydraulic chamber 27. This primary hydraulic chamber 27
The hydraulic pressure is introduced from a hydraulic circuit described later.

The primary pulley 21 is a primary hydraulic chamber.
By moving the movable conical plate 24 in the axial direction by the hydraulic pressure introduced into the inside 27 to increase or decrease the interval between the movable conical plate 24 and the fixed conical plate 23 and changing the groove width of the belt receiving groove 21a, the primary pulley
The winding radius of the belt 20 with respect to 21, that is, the effective radius of the pulley 21 is adjusted.

The secondary pulley 31 has basically the same configuration as that of the primary pulley 21 described above, and has a fixed conical plate on a secondary shaft 32 which is spaced apart from and parallel to the primary shaft 22. 33 is provided integrally with the secondary shaft 32, and a movable conical plate 34 is provided so as to be movable in the axial direction of the secondary shaft 32. The conical friction surface of the fixed conical plate 33 and the conical friction surface of the movable conical plate 34 form a belt receiving groove 31a having a substantially V-shaped cross section.

A cylindrical cylinder 35 is fixed to the outer surface 34a of the movable conical plate 34. A piston 36 fixed to the secondary shaft 32 is oil-tight to the inner surface of the cylinder 35. It is inserted. And this piston
A single-chamber secondary hydraulic chamber 37 is constituted by the cylinder 36, the cylinder 35, and the movable conical plate. As in the primary hydraulic chamber 27, hydraulic pressure is introduced into the secondary hydraulic chamber 37 from a hydraulic circuit.

Similarly to the primary pulley 21, the secondary pulley 31 moves the movable conical plate 34 in the axial direction by hydraulic pressure introduced into the secondary hydraulic chamber 37 to increase or decrease the distance between the movable conical plate 33 and the fixed conical plate 33. By changing the groove width of the belt receiving groove 31a, the winding radius of the belt 20, that is, the effective radius of the pulley 31 is adjusted. In addition,
The pressure receiving area of the movable conical plate 34 is set to be smaller than that of the movable conical plate 24 of the primary pulley 21.

Next, the operation of the continuously variable transmission Z will be described. The torque transmitted from the engine A via the torque converter B is transmitted to the belt transmission mechanism D in the forward / reverse switching mechanism C with the rotation direction set to the forward direction or the reverse direction.

In the belt transmission mechanism D, when the effective radius of the primary pulley 21 is adjusted by introducing or discharging hydraulic oil into the primary hydraulic chamber 27 of the primary pulley 21, the primary pulley 21 is moved via the belt 20. In the secondary pulley 31 that is linked and connected in a linked manner, the effective radius of the secondary pulley 31 is adjusted while following the secondary pulley 31. The speed ratio between the primary shaft 22 and the secondary shaft 32 is determined by the ratio between the effective radius of the primary pulley 21 and the effective radius of the secondary pulley 31.

The rotation of the secondary shaft 32 is further transmitted to the differential mechanism F after being reduced by the reduction mechanism E.
The power is transmitted from the differential mechanism F to the front axle.

The speed reduction mechanism E includes an output gear 38 fixedly mounted on a secondary shaft 32 which is an output shaft of the continuously variable transmission Z, and a differential case of a differential device F which rotates around an axis parallel to the secondary shaft 32. Large-diameter input gear fixed to 39
40, and first and second reduction gears 42 and 43 arranged side by side on a reduction gear shaft 41 parallel to the secondary shaft 32. The first reduction gear 42 is formed to have a larger diameter than the output gear 38 of the secondary shaft 32 meshing with the gear 42,
Further, the second reduction gear 43 meshing with the large-diameter input gear 40 of the differential gear F is formed to have a smaller diameter than the first reduction gear 42, and a large reduction ratio can be obtained by the transmission mechanism E. ing. Both ends of the reduction gear shaft 41 are bearings 44,
It is rotatably supported by 45.

FIG. 3 is a sectional view of a portion below the axis of the secondary shaft 32 of the continuously variable transmission Z. Note that the reference numerals assigned to the respective parts in FIG. 3 correspond to those in FIG.

In FIG. 3, reference numeral 46 denotes a transmission mechanism housing, and 47 denotes a joint housing, which are opposed to each other.
The two housings 46, 47 are joined in a vertical plane 48 and are aligned with respect to a dowel pin 49.

A second reduction gear 43 having the smallest diameter is formed integrally with the reduction gear shaft 41, and the first reduction gear 42 is spline-coupled to the reduction gear shaft 41 so as to rotate integrally. I have. One end (the left end in FIG. 3) of the reduction gear shaft 41 is rotatably supported by a bearing cover 50 via a bearing 44, and the other end (the right end in FIG. 3) of the reduction gear shaft 41 is connected via a bearing 45. It is rotatably supported by the unit housing 47.

The bearing cover 50 has a structure as shown in FIGS.
Bearing support with inner peripheral surface 51a on which 44a fits
51, a flange 52 having a bolt hole 52a for fixing the bearing cover 50 to the joint housing 47 by bolting, and a part of the cylinder projecting from the surface 52b of the flange 52 to the joint housing 47 side. And a projecting edge 53. The outer peripheral surface 53a of the protruding edge 53 is formed coaxially with the inner peripheral surface 51a of the bearing support 51 by simultaneous processing.

On the other hand, as shown in FIG. 1, the bearing housing 51 of the bearing cover 50 is also provided on the joint housing 47 side.
Similarly to the above, a bearing support portion 54 having an inner peripheral surface 54a on which the outer race 45a of the bearing 45 is fitted is formed, and a circular concave portion 55 for accommodating the protruding edge portion 53 of the bearing cover 50 is formed. I have. The inner peripheral surface 55a of the circular recess 55 is connected to the outer peripheral surface 53a of the protruding edge 53 of the bearing cover 50.
It is formed in a dimension where a seal fit is made between
And the inner peripheral surface 55a and the inner peripheral surface 54 of the bearing support 54.
are formed together with the outer peripheral surface 53a of the projecting edge 53 of the bearing cover 50 and the inner peripheral surface 51a of the bearing support 51 by simultaneous processing.

With such a configuration, the joint housing
By fitting the protruding edge 53 of the bearing cover 50 into the recess 55 of the 47 by soldering, both bearing support portions 51, 54 are provided.
The bearing cover 50 is aligned with the inner peripheral surfaces 51a, 54a of the gear shaft 51 being aligned with each other.
Since the bearings 44 and 45 supporting both ends of the shaft 51 are accurately aligned, gear noise generated when the shaft 51 rotates can be significantly reduced. In this embodiment, the present invention is applied to a belt-type continuously variable transmission, but it goes without saying that the present invention can be applied to a transmission having another reduction gear.

[Brief description of the drawings]

FIG. 1 is a sectional view showing a state in which a bearing cover is attached to a joint housing in an embodiment of a reduction gear supporting structure of a transmission according to the present invention .

FIG. 2 is a skeleton diagram showing an overall configuration of a belt-type continuously variable transmission to which a reduction gear supporting structure according to the present invention is applied .

FIG. 3 is a sectional view of the main part.

FIG. 4 is a rear view of the bearing cover .

FIG. 5 is a front view of the bearing cover .

FIG. 6 is a sectional view taken along the line VI-VI of FIG. 4 ;

[Explanation of symbols]

 20 Belt 21 Primary pulley 31 Secondary pulley 32 Secondary shaft (transmission output shaft) 38 Output gear 40 Differential gear input gear 41 Reduction gear shaft 42,43 Reduction gear 44,45 Bearing 46 Transmission mechanism housing 47 Joint housing 50 Bearing cover 51, 54 Bearing support 53 Protrusion 55 Circular recess

──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-1-112076 (JP, A) JP-A-3-92646 (JP, A) JP-A-4-22645 (JP, U) JP-A-50- 123773 (JP, U) Actually open 58-67158 (JP, U) (58) Field surveyed (Int. Cl. ⁷ , DB name) F16H 57/00-57/04

Claims (3)

(57) [Claims] 1. A opposite to the combined transmission mechanism housing and the joint housing and the transmission housed in a casing consisting of the output shaft to each other, and are parallel to one another axle for transmitting power to the wheels Establishment
And disposed between the output shaft and the axle of the transmission, and
A supporting structure of the reduction gear that transmits by decelerating the rotation from the force shaft to the axle, provided in front Symbol transmission mechanism housing and the separate Bearin
And a reduction gear provided on the bearing cover and the bearing cover.
And a bearing for supporting one end portion of the reduction gear shaft, pre SL bearing cover, relative to the joint housing which supports the other end portion of the reduction gear shaft, between the joint housing and the bearing cover A reduction gear support structure for a transmission, wherein the reduction gear support structure is positioned and mounted by formed coaxial fitting means. 2. The coaxial fitting means of the bearing cover and the joint housing comprises a stamping fitting, and the stamping fitting together with each bearing support of the bearing cover and the joint housing. The reduction gear support structure according to claim 1, wherein the reduction gear support structure is formed by processing. 3. The reduction gear supporting structure according to claim 2, wherein the transmission comprises a belt-type continuously variable transmission having a transmission mechanism in which a belt is suspended between two pulleys.