JPH1122809A - Differential device - Google Patents

Abstract

(57) [Problem] To obtain a large initial torque by a compact initial torque applying means having a simple structure and to enhance compatibility. SOLUTION: A bevel gear type differential mechanism 33, which connects output side gears 27, 29 via a pinion gear 25 supported on a pinion shaft 19 supported on a differential case 3, and receives a meshing reaction force of the gears 27, 29. Differential limiting clutches 35 and 37 and gears 27 and 2
And a disc spring 5 that applies initial torque to the clutches 35 and 37.
7, the holder 55 is provided with a support portion 59 supported by the gear 25, a through hole 63 through which the shaft 19 passes, and a concave portion 67 that supports the outer periphery of the disc spring 57.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a differential device for a vehicle.

[0002]

2. Description of the Related Art Japanese Patent Publication No. 46-8206 discloses a differential device 201 as shown in FIG.

[0003] The differential device 201 includes a pinion shaft 205 fixed to a differential case 203,
A bevel gear type differential mechanism 213 including a pinion gear 207 rotatably supported on a pinion shaft 205 and output side gears 209 and 211 meshing with the pinion gear 207 is provided.
1 is spline-connected to the respective drive shafts 215, 217 so as to be movable.

Press-side clutch members 219 and 219 are movably spline-connected to the drive shafts 215 and 217, and pressure-receiving clutch members 221 and 221 are fixed to the differential case 203. The conical clutch 2 is provided between the clutch members 219 and 221 respectively.
23 and 223 are formed. These conical clutches 223 are engaged by receiving the meshing reaction force of the side gears 209 and 211, and limit the differential of the differential mechanism 213.

A plurality of coil springs 227 held by a pair of retainers 225, 225 are arranged between the side gears 209, 211. Pinion shaft 2
05 penetrates through holes 229 of each retainer 225. Each coil spring 227 is connected to the conical clutch 22 via retainers 225 and 225 and side gears 209 and 211.
3, 223 to give initial torque,
It improves the ability of vehicles to travel and escape on rough roads.

[0006]

However, in the differential device 201, in each of the retainers 225, the holding portion 231 of the coil spring 227 and the side gears 209, 21 are provided.
Since the first pressing portion 233 is far apart, each retainer 225 must have sufficient rigidity to prevent deformation, and if the rigidity is insufficient, the conical clutches 223 and 22
3 cannot be pressed strongly, so that a large initial torque cannot be obtained.

On the other hand, if the rigidity is increased, the retainer 225 becomes thicker, so that a wider space is required and the weight increases, which is disadvantageous.

Further, in order to obtain a large pressing force with the coil spring 227, it is necessary to increase the size of the coil spring 227 or to use a plurality of the coil springs 227 as described above. Become wider.

Therefore, unless the size of the differential device 201 is increased, it becomes impossible to establish the differential device 201 using the retainer 225 and the coil spring 227.

[0010] For this reason, the differential case 203 and the differential mechanism 21 are used to determine whether the initial torque is obtained by using the retainer 225 and the coil spring 227 or not.
3. It is impossible to share the conical clutches 223 and 223, and the compatibility is low.

[0011] Each retainer 225 is provided with a coil spring 22.
7 and the through hole 2 of the pinion shaft 205.
Since 29 and the like are required, the shape is complicated, and the cost is increased by the number of molding steps.

Accordingly, an object of the present invention is to provide a differential device which can obtain a large initial torque by means of an initial torque applying means which is compact and has a simple structure and has high compatibility.

[0013]

According to the first aspect of the present invention,
A bevel gear having a differential case that is rotationally driven by the driving force of the engine, a pinion shaft supported by the differential case, a pinion gear supported on the pinion shaft, and a pair of output side gears connected to each other via the pinion gear. A differential device comprising a differential mechanism of the type and a clutch for limiting a differential, which is provided between the side gear and the differential case and is engaged by receiving a meshing reaction force of the side gear, wherein each side gear and a pinion gear are formed. A holder arranged in the space to be
A disc spring that is supported by the holder and presses the clutch via a side gear to apply an initial torque; a support portion supported by the inner surface of the pinion gear and the disc spring are fitted to the holder; And a concave portion for performing the operation.

The driving force of the engine for rotating the differential case is distributed from the pinion shaft to both side gears via the pinion gears, transmitted to the respective wheel sides, and the clutch is engaged by receiving the reaction force of the engagement of the side gears. The resistance limits the differential of the differential mechanism.

Further, the clutch is pressed by the disc spring via each side gear to obtain an initial torque.

In the differential device according to the first aspect of the present invention, since the holder for the disc spring is provided with the support portion supported by the inner surface of the pinion gear, the holder is provided in a space formed between each side gear and the pinion gear. And a side gear can be directly pressed by a disc spring for centering the concave portion of the holder.

In this manner, the initial torque is
Unlike the prior art, which is affected by the rigidity of the clutch 25, in the differential device of the present invention, since the retainer is not interposed between the disc spring and the clutch, the clutch can be strongly pressed by the disc spring, and a large initial torque can be obtained. Can be

Further, since the retainer is not used, a problem of a large arrangement space, an increase in weight, and an increase in the size of the differential device are prevented.

Further, as described above, since the holder is arranged in the space between each side gear and the pinion gear, the holder and the disc spring are used (the one that obtains the initial torque).
A differential case, a differential mechanism, a clutch, and the like can be shared between a device that does not use (a device that does not obtain initial torque) and a device that does not use it (initial torque), and compatibility is greatly improved.

Also, by using a disc spring that is thin and provides a large pressing force instead of a coil spring, the holder and the disc spring are arranged in a narrow space between the side gear and the pinion gear as described above. As a result, a sufficiently large initial torque can be obtained while maintaining compatibility.

Further, since a member having a complicated shape such as the retainer 225 is not used, the cost is reduced accordingly.

According to a second aspect of the present invention, in the differential device according to the first aspect, the holder is provided with an engagement hole with which a pinion shaft is engaged. To get the effect.

[0023] In addition, by providing the holder with an engagement hole with which the pinion shaft engages, it becomes easier to dispose the holder in the space between each side gear and the pinion gear.

Further, since the holder and the pinion shaft support each other by engaging the pinion shaft with the engagement hole of the holder, the supporting strength of each is improved, which is advantageous.

According to a third aspect of the present invention, there is provided the differential device according to the second aspect, wherein the holder and the disc spring have penetrating holes through which the drive shafts connected to the respective side gears penetrate. And the pinion shaft can be abutted against each other, and the same effect as that of the second aspect is obtained.

In addition, since the holder and the disc spring have penetrating holes through which the drive shaft penetrates, the drive shaft can be abutted against the pinion shaft, and there is no need to change the drive shaft.

Thus, also in this respect, the compatibility between the one using the holder and the one using the disc spring and the one not using it are advantageous.

[0028]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described with reference to FIGS. This embodiment is described in claims 1, 2, and 3.
It has the following features. FIG. 1 shows a differential device 1 of this embodiment, and the left and right directions are the left and right directions in FIG. In addition, members and the like without reference numerals are not shown.

As shown in FIG. 1, the differential case 3 of the differential device 1 is constituted by fixing a casing body 5 and a cover 7 with bolts 9.

The differential case 3 is arranged inside the differential carrier, and the left and right boss portions 11, 13 are respectively supported by the differential carrier via bearings. This differential carrier is provided with an oil sump, and the boss 1
Spiral oil grooves 15 and 17 for guiding oil from the oil reservoir to the inside of the differential case 3 are provided on the inner periphery of the oil reservoirs 1 and 13.

A ring gear is fixed to the differential case 3 with bolts. The ring gear meshes with a driving gear of a driving force transmission system, and the differential case 3 is driven to rotate by the driving force of the engine via the driving force transmission system.

A pinion shaft 19 is arranged inside the differential case 3. The outer end of the pinion shaft 19 is fitted into the through hole 21 of the differential case 3, and the pinion shaft 19 is prevented from coming off and rotating by a spring pin 23. Have been. A pinion gear 25 is rotatably supported on the pinion shaft 19. Side gears 27 and 29 on the output side from right and left mesh with the pinion gear 25, and the side gears 27 and 29 are spline-connected to respective drive shafts so as to be movable.

A spherical washer 31 is provided between the pinion gear 25 and the differential case 3 for receiving the centrifugal force and the meshing reaction force of the pinion gear 25. The side gears 27 and 29 are supported from the radial outside by meshing with the pinion gear 25.

Thus, the bevel gear type differential mechanism 33 is constituted.

The driving force of the engine for rotating the differential case 3 is distributed from the pinion shaft 19 to the side gears 27 and 29 via the pinion gear 25 and transmitted to the left and right wheels via the respective drive shafts. Further, for example, when a driving resistance difference occurs between the wheels during traveling on a rough road, the driving force of the engine is differentially distributed to the left and right sides by the rotation of each pinion gear 25.

Conical clutches 35 and 37 (clutches) are provided between the side gears 27 and 29 and the differential case 3, respectively.
Are formed. Conical clutch 3 on side gear 27 side
Reference numeral 5 denotes a conical surface 39, 41 formed on the cover 7 and the side gear 27, respectively, and a conical clutch 37 on the side gear 29 side includes conical surfaces 43, 45 formed on the casing body 5 and the side gear 29, respectively. .

The conical surfaces 39, 41 of the conical clutch 35
A taper ring 47 is disposed between the conical clutch 37 and the conical surfaces 43 and 45 of the conical clutch 37. As described below, each tapered ring 47 is prevented from rotating with respect to the differential case 3, and the inner periphery of each tapered ring 47 is
It slides with 1 and 45.

When torque is applied to the differential device 1, the taper ring 47 is sandwiched by the meshing reaction force generated in the side gears 27 and 29, and the conical clutches 35 and
37 is pressed and fastened, and the differential of the differential mechanism 33 is limited by these frictional resistances.

As shown in FIG. 2, the cover 7 has four openings 4.
9 are provided at equal intervals in the circumferential direction, and as shown in FIG. 3, four openings 51 are provided at equal intervals in the circumferential direction in the casing body 5.

As the differential case 3 rotates, the oil in the oil sump flows into the differential case 3 from these openings 49 and 51 and the oil grooves 15 and 17 of the boss portions 11 and 13, and each gear of the differential mechanism 33. The lubrication of the meshing part, the sliding part, the conical clutches 35 and 37, and the like are performed. In particular, each opening 4
The oils 9 and 51 are arranged directly adjacent to the conical clutches 35 and 37, so that oil is directly supplied to them and sufficient lubrication is performed.

Each taper ring 47 has four claws 53
Are formed at equal intervals in the circumferential direction.
7, the pawls 53 are engaged with the cover 7 and the openings 49 and 51 of the casing body 5 to prevent rotation.

As shown in FIG. 1, a holder 55 is provided in a space formed between the pinion gear 25 and each of the side gears 27, 29.
And a disc spring 57 are disposed.

As shown in FIGS. 4 and 5, the holder 55 has a pair of parallel support portions 59, 59 and a pair of parallel surfaces 61, 61.
And the through holes 63 (engagement holes) penetrating the support portions 59, 59
, Penetration holes 65, 65 through which the drive shafts connected to the side gears 27, 29 penetrate, and recesses 67, 67 into which the disc spring 57 is fitted.

Each support portion 59 of the holder 55 is slidably supported by an inner end face of the pinion gear 25.

The pinion shaft 19 passes through the through hole 63 of the holder 55, and the holder 55 and the pinion shaft 19 support each other.

As shown in FIGS. 6 and 7, the disc spring 57 also has a penetration hole 69 through which the drive shaft penetrates.

The drive shafts of the side gears 27 and 29 penetrate through the through holes 65 and 69 of the holder 55 and the disc spring 57 and abut against the pinion shaft 19 to be positioned.

The disc spring 57 fits into the recess 67 of the holder 55 and supports (centers) the outer periphery 71 thereof.
The side gears 27, 29 are pressed directly in the direction of the respective conical clutches 35, 37.

The disc spring 57 is linear in the amount of flexure and the spring force, and generates a large pressing force with a slight flexure. Due to the pressing force of the disc spring 57, each of the conical clutches 35, 37
Is fastened to generate an initial torque, and the running performance and the escape performance of the vehicle on a rough road and the like are greatly improved.

Thus, the differential device 1 is configured.

In the differential device 1, as described above, the holder 55 supports the support portion 59 supported by the pinion gear 25 and the through-hole 63 through which the pinion shaft 19 passes.
Is provided, the holder 55 can be connected to each side gear 2.
Each of the side gears 27 and 29 can be directly pressed by a disc spring 57 supported by a concave portion 67 of the holder 55, while being able to be arranged in the space between the pinion gear 25 and the pinion gear 25.

Therefore, the initial torque is
Unlike the conventional example which is affected by the rigidity of No. 5, the disc spring 57 presses each of the conical clutches 35 and 37 without passing through the retainer, so that it can be pressed with a large force and a sufficient initial torque can be obtained.

Further, since the retainer is not used, a problem of a large arrangement space, an increase in weight, and an increase in the size of the differential device 1 are prevented.

As described above, the holder 55 and the disc spring 5
7 is disposed in the space between the side gears 27 and 29 and the pinion gear 25, so that the differential case 3 and the differential mechanism can be used between the holder 55 and the one that does not use the disc spring 57 to obtain the initial torque. 33, cone clutch 35,
37 can be shared, and compatibility is greatly improved.

Also, unlike the conventional example, the use of the disc spring 57, which is thin and provides a large pressing force, instead of the coil spring, also makes the side gears 27, 29 as described above.
The holder 55 and the disc spring 57 can be arranged in a narrow space between the pinion gear 25 and the pinion gear 25, and a sufficiently large initial torque can be obtained while maintaining compatibility.

Further, since the retainer 225 having a complicated shape is not used, the cost is reduced accordingly.

In addition to this, as described above, the holder 55
The pinion shaft 19 penetrates the through hole 63, and the holder 55 and the pinion shaft 19 support each other, so that the support strength of each is improved, which is advantageous.

Further, since the holder 55 and the disc spring 57 are provided with the penetration holes 65 and 69 through which the drive shaft penetrates, it is possible to position the drive shaft by abutting the pinion shaft 19, and it is necessary to change the drive shaft. There is no.

Also in this respect, the compatibility between the one using the holder 55 and the one using the disc spring 57 and the one not using it is advantageous.

The parallel surfaces 61 of the holder 55 may be curved surfaces instead of flat surfaces.

Unlike the embodiment, the support (centering) of the disc spring by the holder may be performed not on the outer periphery but on the inner periphery.

In the present invention, the clutch is not limited to the conical clutch, but may be, for example, a multi-plate clutch.

Further, the differential device of the present invention
Front differential (differential device that distributes engine driving power to left and right front wheels) and rear differential (differential device that distributes engine driving force to left and right rear wheels)
And a center differential (a differential device that distributes the driving force of the engine to the front wheels and the rear wheels).

[0064]

According to the differential device of the first aspect,
By disposing the disc spring holder in the space formed between each side gear and the pinion gear and allowing the side gear to be directly pressed by the disc spring supported by this holder, unlike the conventional example, the retainer can be used. The clutch can be strongly pressed without any intervention, and a large initial torque can be obtained.

Further, since the retainer is not used, a problem of a large arrangement space, an increase in weight, and an increase in the size of the differential device are prevented.

Further, as described above, since the holder and the disc spring are arranged in the space between each side gear and the pinion gear, the differential case, the differential mechanism, It becomes possible to share a clutch and the like, and compatibility is greatly improved.

In addition, the use of a thin disk spring with a large pressing force instead of a coil spring makes it possible to dispose the holder and the disk spring in a narrow space between the side gear and the pinion gear. A sufficiently large initial torque can be obtained while maintaining the characteristics.

Further, since a retainer having a complicated shape is not used, the cost is reduced accordingly.

According to the second aspect of the invention, the same effect as that of the first aspect is obtained.

Further, since the holder is provided with an engagement hole with which the pinion shaft engages, the holder can be more easily arranged in the space between each side gear and the pinion gear, and the pinion shaft can be engaged with the engagement hole of the holder. By joining, the holder and the pinion shaft support each other,
Each supporting strength is improved, which is advantageous.

According to the third aspect of the present invention, the same effect as that of the second aspect is obtained, and a penetrating hole through which the drive shaft penetrates is provided in the holder and the disc spring. Is possible,
Since there is no need to change the drive shaft, this is also advantageous in that the compatibility between the holder and the one without the disc spring is maintained.

[Brief description of the drawings]

FIG. 1 is a sectional view showing an embodiment of the present invention, and FIG.
AA sectional view of FIG.

FIG. 2 is a view on arrow B of FIG. 1;

FIG. 3 is a view taken in the direction of arrow C in FIG. 1;

FIG. 4 is a front view of a holder used in the embodiment of FIG.

FIG. 5 is a sectional view taken along the line DD of FIG. 4;

FIG. 6 is a front view of a disc spring used in the embodiment of FIG. 1;

FIG. 7 is a sectional view taken along the line EE of FIG. 6;

FIG. 8 is a sectional view of a conventional example.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 Differential device 3 Differential case 19 Pinion shaft 25 Pinion gear 27, 29 Output side gear 33 Bevel gear type differential mechanism 35, 37 Conical clutch (clutch) 55 Holder 57 Disc spring 59 Supporting portion by pinion gear 63 Penetration of holder through which pinion shaft passes Hole (engagement hole) 65 Penetration hole of holder into which drive shaft penetrates 67 Depression of holder into which disc spring fits 69 Penetration hole of disc spring into which drive shaft penetrates 71 Outer periphery of disc spring

Claims (3)

[Claims] 1. A differential case rotatably driven by the driving force of an engine, a pinion shaft supported by the differential case, a pinion gear supported on the pinion shaft, and a pair of output sides connected to each other via the pinion gear. A differential device comprising: a bevel gear type differential mechanism having a side gear; and a differential limiting clutch provided between the side gear and the differential case and engaged by receiving a meshing reaction force of the side gear. And a holder disposed in a space formed by the pinion gear and a disc spring supported by the holder and pressing the clutch via a side gear to apply an initial torque.The holder is supported by an inner surface of the pinion gear. And a recess for fitting a disc spring and centering it. A differential device characterized by being provided. 2. The differential device according to claim 1, wherein the holder has an engagement hole with which a pinion shaft is engaged. 3. The invention according to claim 2, wherein the drive shaft and the pinion shaft abut against each other by providing a penetration hole through which the drive shaft connected to each side gear penetrates in the holder and the disc spring. A differential device characterized by being made possible.