JP2825447B2 - Differential device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a differential device for allowing a rotational difference between left and right driving wheels or front and rear driving wheels of an automobile.

[0002]

2. Description of the Related Art Conventionally, a differential device used in a driving force transmission system of an automobile is a device that allows a difference in rotation between left and right drive wheels when traveling on a curve or a difference in rotation between front and rear drive wheels in a four-wheel drive vehicle. However, if only one of the driving wheels rides on a road surface with extremely low friction coefficient, such as snow or sand, the wheels will spin and the entire driving force will be lost, making it impossible to escape from the place. It was easy. Further, even when the load on the inner wheels is extremely reduced due to centrifugal force when traveling at high speed on a curve, there is a disadvantage that the wheels spin and the driving force for traveling at high speed on the curve is easily lost. . Therefore, in order to compensate for such a drawback, there is, for example, a type provided with a differential limiting mechanism such as a clutch disk press-fit type, which limits the differential of each drive wheel under predetermined conditions. However, in this type, an abrupt differential limiting effect is exhibited with an increase in the rotational difference, and when the differential is limited, the respective driving wheels are restrained even when the driving force is not input from the engine side. Therefore, there has been a problem in combination with a device that requires independence in rotation of each wheel, such as an anti-lock brake system.

Therefore, while limiting the differential under predetermined conditions during driving, while maintaining the independence of the rotation of each driving wheel during non-driving, a rotational speed sensitive type using a viscous coupling has recently been used. Are often used. The viscous coupling is a kind of viscous clutch, which transmits torque using the shear resistance of viscous fluid (silicon oil etc.), so that a smooth differential limiting effect can be obtained according to the rotation difference. .

A differential device having a mechanism for restricting the differential only during driving without restraining each driving wheel when not driving is disclosed in, for example, JP-A-4-271926. A torque-sensitive type using a combination of a worm gear is also known. In this type, a pair of screw-shaped worms rotatable independently of each other on the same axis and a plurality of worm wheels having a rotation axis perpendicular thereto are engaged with each other, and when each worm is rotated, the worm wheel becomes It utilizes the unique characteristics of a worm gear, which rotates smoothly but conversely makes it difficult to rotate from the worm wheel side, thereby achieving differential and differential limiting effects according to conditions. It has the feature that it can be done.

[0005]

However, in a differential device with a rotational speed sensitive type differential limiting mechanism represented by a viscous coupling, the torque transmission rate depends on the viscosity of the fluid. There is a disadvantage that the viscosity of the fluid changes and a stable differential limiting effect cannot always be obtained. Further, in this type, there is a time lag between the occurrence of the rotation difference and the execution of the differential limitation, and there is a problem that it is not possible to instantaneously respond to a change in the running operation. On the other hand, in a differential device using a worm gear, the differential limiting effect is stable because the differential limiting is performed mechanically, but on the other hand, the number of parts is large and the structure is complicated, and the processing of parts and There has been a problem that extremely high accuracy is required for assembly, and the entire device becomes larger than the allowable torque.

SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned problems, and an object of the present invention is to provide a small and low-cost differential device which can obtain a reliable differential limiting effect with a simple structure. Is to provide.

[0007]

In order to achieve the above object, according to the present invention, an input-side rotator that rotates about an axis by a driving force input from the outside, An eccentric rotator held on the input rotator so as to be rotatable about an axis eccentric to the axis, and disposed on the axis of the input rotator facing both end surfaces of the eccentric rotator. A pair of output-side rotating bodies, a plurality of rolling bodies held in a large number of holes provided at equal intervals in a circumferential direction on both end surfaces of the eccentric rotating body, and a plurality of rolling bodies held in the eccentric rotating body. A guide portion that partially protrudes from both end surfaces of the eccentric rotator at predetermined positions in the circumferential direction of the eccentric rotator, and a reversing mechanism that converts the rotation of one output-side rotator in the opposite direction and transmits the rotation to the outside, Each output side rotator rotates eccentrically when each output side rotator rotates in the same direction. Constitute a differential device having a plurality of grooves that rotates in a predetermined direction eccentric rotor by guiding the rolling elements projecting from both end faces of the.

According to a second aspect of the present invention, an input-side rotating body that rotates around an axis by a driving force input from the outside, and a state in which the input-side rotating body is rotatable about an axis that is eccentric with respect to the axis of the input-side rotating body. A pair of eccentric rotators held by the input rotator, and a pair of output sides disposed on the axis of the input rotator with one end face of each eccentric rotator interposed therebetween. A rotating body, a large number of rolling bodies held in a large number of holes provided at equal intervals in the circumferential direction on one end surface of each eccentric rotating body, and a part of the rolling bodies held by each eccentric rotating body A guide portion projecting from one end surface of the eccentric rotator at a predetermined position in the circumferential direction of the eccentric rotator, and a reversing mechanism for converting the rotation of each eccentric rotator into a direction opposite to each other. When the output side rotating bodies rotate in opposite directions, they protrude from one end face of each eccentric rotating body. Constitute a differential device having a plurality of grooves to guide the rolling elements each eccentric rotary body is rotated in the opposite directions that.

According to a third aspect of the present invention, the input-side rotator that rotates around the axis by the driving force input from the outside, and the input-side rotator that is rotatable about the axis of the input-side rotator. A pair of eccentric rotations arranged with one end face facing each end face of the driven rotator while being rotatable about an axis eccentric to the axis of the held driven rotator and the input-side rotator. Body, a pair of output-side rotators disposed on the axis of the input-side rotator with each eccentric rotator interposed therebetween, and a plurality of eccentric rotators provided at equal circumferential intervals on one end surface of each eccentric rotator. A large number of rolling elements held so as to be able to come and go in the holes, and a guide part for projecting a part of the rolling elements held by each eccentric rotator from one end surface of the eccentric rotator at a predetermined circumferential position of the eccentric rotator; The rotation of each eccentric rotator is directed in the positive direction to one output side rotator, and the other output side rotator Is provided with a reversing mechanism that converts and transmits in the opposite direction, and when the eccentric rotating bodies rotate in the same direction with each other, the driven rotating body guides the rolling elements protruding from both end faces of the eccentric rotating body to perform the driven rotation. The differential device is provided with a number of grooves for rotating the body in a predetermined direction.

According to a fourth aspect of the present invention, an input-side rotator that rotates around an axis by a driving force input from the outside, and a state in which the input-side rotator can rotate around an axis eccentric with respect to the axis of the input-side rotator. An eccentric rotator held on the input rotator, a pair of output rotators arranged on the axis of the input rotator with one end face facing each end face of the eccentric rotator, and each output side A large number of rolling elements held in a large number of holes provided at equal intervals in the circumferential direction on one end surface of the rotating body and a large number of rolling elements, and a part of the rolling elements held by each output-side rotating body are formed by an eccentric rotating body. A guide portion projecting from both end surfaces of the eccentric rotator at a predetermined position in the circumferential direction, and a reversing mechanism for converting the rotation of one output-side rotator into a reverse direction and transmitting the rotation to the outside, wherein the eccentric rotator has When the output side rotating bodies rotate in the same direction as each other, they protrude from one end face of each output side rotating body. Constitute a differential device having a plurality of grooves that rotates in a predetermined direction eccentric rotor by guiding the rolling elements that.

According to a fifth aspect of the present invention, an input-side rotator that rotates around an axis by a driving force input from the outside, and a state in which the input-side rotator can rotate about an axis eccentric with respect to the axis of the input-side rotator. An eccentric rotator held by the input rotator, a pair of output rotators arranged on the axis of the input rotator with one end face facing both end surfaces of the eccentric rotator, and an eccentric rotator A large number of rolling elements held in a large number of holes provided at equal intervals in the circumferential direction on both end faces of the rolling element, and a part of the rolling elements held by the eccentric rotating body are positioned at predetermined positions in the circumferential direction of the eccentric rotating body. And a guide portion projecting from both end surfaces of the eccentric rotating body.Each output-side rotating body has a rolling element that projects from one end face of each output-side rotating body when each output-side rotating body rotates in the opposite direction to each other. A differential device provided with a number of grooves for guiding and rotating the eccentric rotating body in a predetermined direction It is configured.

[0012]

According to the differential device of the first aspect, when the input-side rotator rotates around the axis by an external driving force, the eccentric rotator rotates about the axis of the input-side rotator. The torque is transmitted to each output-side rotator via a rolling element that fits into a groove of each output-side rotator. Here, when a rotation difference occurs between the drive shafts on the output side, the groove of each output side rotating body rolls the rolling element, and the eccentric rotary body follows the rolling of the rolling element and the output side rotating body and each output side rotating body. Rotate in the same direction. In this case, the rotation of one output-side rotator is converted to the opposite direction via the reversing mechanism, and each output-side rotator rotates in the same direction as each other, thereby achieving the differential of each drive shaft. At that time, when a force causing a rotation difference is applied to each output-side rotating body from only one output-side rotating body, the other output-side rotating body forms a groove on which the driven-side rolling element at the time of differential is the driven side. In order to follow its own movement, the rolling element receives a reaction force from the groove, which acts as a resistance, thereby limiting the differential between the output side rotating bodies.

According to the second aspect of the present invention, when the input-side rotator rotates around the axis by an external driving force, each eccentric rotator rotates about the axis of the input-side rotator. Then, this rotational force is transmitted to each output-side rotator via a rolling element fitted into a groove of each output-side rotator. Here, when a rotation difference occurs in each drive shaft on the output side, the groove of each output side rotating body rolls the rolling element, and each eccentric rotary body follows the rolling of the rolling element and outputs a corresponding output. It rotates in the same direction as the side rotator. In this case, the rotations of the respective eccentric rotary members are converted in the opposite directions via the reversing mechanism, and the respective output side rotary members rotate in the opposite directions to achieve the differential of the respective drive shafts. At that time, when a force causing a rotation difference is applied to each output-side rotating body from only one output-side rotating body, the other output-side rotating body forms a groove on which the driven-side rolling element at the time of differential is the driven side. In order to follow its own movement, the rolling element receives a reaction force from the groove, which acts as a resistance, thereby limiting the differential between the output side rotating bodies.

According to the third aspect of the present invention, when the input-side rotator rotates around the axis by an external driving force, each eccentric rotator rotates about the axis of the input-side rotator. This rotational force is transmitted to each output side rotating body. Here, when a rotation difference occurs in each drive shaft on the output side, each eccentric rotator rotates in the same direction with respect to the axis eccentric with respect to the axis of the input rotator, and each eccentric rotator rotates on each eccentric rotator. The held rolling element rolls along the groove of the driven rotator, and the driven rotator follows the rolling of the rolling element and rotates in the same direction as each eccentric rotator. In this case, the rotation of one of the output-side rotators is converted to the opposite direction via the reversing mechanism, and the output-side rotators rotate in opposite directions to achieve the differential of the respective drive shafts.
At that time, when a force that causes a rotation difference is applied to each output side rotating body from only one of the output side rotating bodies, the driven rotating groove in the driven rotating body is the driven side at the time of the differential. This groove receives a reaction force from the rolling element, which acts as a resistance, thereby limiting the differential of each output side rotating element.

Further, according to the differential device of the fourth aspect, when the input-side rotating body rotates around the axis by an external driving force, the eccentric rotating body rotates about the axis of the input-side rotating body. This rotational force is transmitted to each output-side rotator via a groove fitted to the rolling element of each output-side rotator. Here, when a rotation difference occurs between the output-side drive shafts, the rolling elements of the output-side rotating bodies roll along the grooves, and the eccentric rotating bodies follow the rolling of the rolling elements, thereby causing each output-side rotating body to rotate. Rotates in the same direction as the body. In this case, the rotation of one output-side rotator is converted to the opposite direction via the reversing mechanism, and each output-side rotator rotates in the same direction as each other, thereby achieving the differential of each drive shaft. At that time, when a force causing a rotation difference is applied to each output side rotating body from only one of the output side rotating bodies, in the eccentric rotating body, the groove which is the driven side at the time of the differential is driven by the rolling element which is the driving side by itself. This groove receives a reaction force from the rolling element, which acts as a resistance, thereby limiting the differential of each output side rotating element.

According to the differential device of the fifth aspect, when the input-side rotating body rotates around the axis by an external driving force, the eccentric rotating body rotates about the axis of the input-side rotating body. This rotational force is transmitted to each output-side rotator via a rolling element fitted into a groove of each output-side rotator. Here, when a rotation difference occurs between the output-side drive shafts, the groove of each output-side rotating body causes the rolling element to roll, and the eccentric rotating body follows the rolling of the rolling element, causing one output-side rotating body to rotate. Rotate in the same direction as. In this case, since the groove of the other output side rotating body is formed so as to rotate in the opposite direction to the eccentric rotating body, each output side rotating body rotates in the opposite direction to each other, and the differential of each drive shaft is reduced. Achieved. At that time, when a force causing a rotation difference is applied to each output-side rotating body from only one output-side rotating body, the other output-side rotating body forms a groove on which the driven-side rolling element at the time of differential is the driven side. In order to follow its own movement, the rolling element receives a reaction force from the groove, which acts as a resistance, thereby limiting the differential between the output side rotating bodies.

[0017]

Embodiment 1 FIGS. 1 to 10 show a first embodiment of the present invention. FIGS. 1 to 3 are sectional views of a differential device, and FIGS. 4 and 5 are exploded perspective views thereof. Note that the dashed lines in FIGS. 4 and 5 indicate that they are continuous with the same numbers corresponding to the respective figures.

This differential gear includes a gear case 1 as an input-side rotating body which is rotated by a driving force from the outside, a gear case cover 2 for closing one end of the gear case 1, and a coaxial shaft opposing each other inside the gear case 1. A pair of output disks 3 and 4 disposed on the eccentric disk 5, an eccentric disk 5 disposed between the output disks 3 and 4, a large number of balls 6 as rolling elements supported on the eccentric disk 5 so as to be able to come and go; A pair of guard rings 7 covering the peripheral edge of the disk 5, a disk holder 8 rotatably supporting the eccentric disk 5, a bevel gear 9 arranged concentrically opposite one output disk 3, and a bevel gear 9 and the output disk 3, a total of four pinion gears 10, a pinion shaft 11 that supports each pinion gear 10, and a ring mounted outside the gear case 1. And a Gugiya 12.
A pair of drive shafts (not shown) is arranged on the rotation axis (hereinafter referred to as a main shaft) of the gear case 1, and each drive shaft is coupled to the other output disk 4 and the bevel gear 9, respectively.

The gear case 1 is formed of a cylindrical member having one end opened, and a through portion 1a through which one drive shaft passes is provided at the other end. A flange 1b is formed in the opening of the gear case 1, and the flange 1b is provided with a number of holes 1c for bolt insertion. Gear case 1
Receiving groove 1d for supporting the pinion shaft 11
Is provided.

The gear case cover 2 is formed in a disk shape.
At the center thereof, a bearing 2a through which a part of the other output disk 4 penetrates is provided. A flange 2b is formed on the periphery of the gear case cover 2, and the flange 2b is provided with a number of holes 2c for bolt insertion.

The output disk 3 has a smooth surface facing the eccentric disk 5, and a bevel gear 3a connected to each pinion gear 10 is formed on the opposite side. Each ball 6 is provided on the surface facing the eccentric disk 5.
Are provided, and each ball groove 3b is formed so as to draw a curve with a predetermined curvature in the same direction. The peripheral edge of the output disk 3 faces a step in the gear case 1, and a thrust washer 3 c is interposed between the facing surface and the gear case 1.

The other output disk 4 has a smooth surface facing the eccentric disk 5, and a coupling portion 4a with one drive shaft is provided on the opposite side. Also,
Each ball 6 is provided on the surface facing the eccentric disk 5 as described above.
Are provided, and each ball groove 4b is formed so as to draw a curve with a predetermined curvature in the same direction. In this case, the ball grooves 3 of each of the output disks 3 and 4
Although b and 4b are curved in the same direction in a single part, they are opposed to each other after assembly, so that when they are overlapped in the axial direction, they are curved in opposite directions. The output disk 4 has a coupling portion 4a inserted into a bearing 2a of the gear case cover 2, and a thrust washer 4c is interposed between the rear surface and the gear case cover 2.

The eccentric disk 5 has smooth surfaces on both sides, and these surfaces are slidably opposed to the output disks 3 and 4. The central portion in the axial direction of the eccentric disk 5 is formed to have a small diameter, and this portion is supported by the disk holder 8 so as to be held eccentric by a predetermined distance from the central axis (main axis) of each of the output disks 3 and 4. You. On both sides of the eccentric disk 5, a large number of ball holes 5a for accommodating the respective balls 6 are provided at equal intervals in the circumferential direction, and the depth of each of the ball holes 5a is formed slightly smaller than the outer diameter of each of the balls 6. Have been.

Each ball 6 has a ball hole 5 of the eccentric disk 5.
It has an outer diameter slightly smaller than a, and is housed in a state where it can freely come and go in each ball hole 5a.

Each guard ring 7 is formed in an L-shaped cross section, and covers the periphery of the eccentric disk 5. A guard wall 7a that covers the ball hole 5a of the eccentric disk 5 is provided in a circumferential half of each guard ring 7, and the guard wall 7a prevents the half ball 6 in the circumferential direction from projecting from the ball hole 5a. I have. In addition, each guard ring 7
Is fixed to a disk holder 8 described later by a protruding piece 7b provided at the peripheral end.

The disk holder 8 is composed of a pair of semicircular members divided in the radial direction, and the small-diameter portion of the eccentric disk 5 is sandwiched from both sides in the radial direction to form the eccentric disk 5.
Is rotatably supported. The outer peripheral surface of the disk holder 8 is formed around the main shaft, while the inner peripheral surface supporting the eccentric disk 5 is formed around an axis that is eccentric by a predetermined distance from the main shaft. The disk holder 8 is fixed in the gear case 1 by a pin 8a fitted into a concave portion on the outer periphery. The eccentric disk 5 is provided on both sides of the disk holder 8.
Guide ring 8b for receiving the ball 6 of each guard ring 7
And the ball 6 of the eccentric disk 5 is received by the guard wall 7a in the guide groove 8b by an amount protruding toward the disk holder 8 side. In this case, the portion of the ball 6 without the guard wall 7a protrudes toward the output disks 3 and 4 by the flat portion of the disk holder 8. Thereby, the eccentric disk 5
The balls 6 arranged on both sides of each of the output disks 3 and 4 are fitted into the ball grooves 3b and 4b of each output disk 3 and 4 by half in the circumferential direction.

The bevel gear 9 has a gear formed on the surface facing one output disk 3, and a coupling portion 9a with the other drive shaft is provided at the center thereof. Also, bevel gear 9
Thrust washer 9b between the back of
Is interposed.

Each of the pinion gears 10 is constituted by a bevel gear, and is disposed around a main shaft by a pinion shaft 11 so that it can rotate around an axis orthogonal to the main shaft. The bevel gear 9 and the bevel gear 3a of the output disk 3 are connected to both sides of each pinion gear 10, respectively. The rotation of the bevel gear 9 is converted in the opposite direction by each pinion gear 10 and transmitted to the output disk 3 side. ing.

The pinion shaft 11 is connected to each pinion gear 1
There is a total of four support shafts 11a that rotatably support the shaft 0, and a pinion gear 10 and a washer 11b are inserted into each of the support shafts 11a. The pinion shaft 11 is fixed to the gear case 1 by receiving the tip of each support shaft 11 a in the receiving groove 1 d of the gear case 1.

The ring gear 12 has one end surface formed by a gear, and has an inner diameter slightly larger than the outer diameter of the gear case 1. A screw hole 12a is provided in the other end surface of the ring gear 12, and a bolt 12b passing through the holes 1c, 2c of the gear case 1 and the gear case cover 2 is screwed into the screw hole 12a of the ring gear 12, so that the gear case 1 and the gear case cover 2 are formed. And the ring gear 12 are integrally connected.

In the differential constructed as described above, as shown in FIG.
2 transmitted to the gear case 1 through the gear case 1
Rotates around the main shaft, and the pinion shaft 11 rotates integrally with the gear case 1. As a result, the driving force transmitted to the pinion shaft 11 is distributed to the bevel gear 9 and one output disk 3 via each pinion gear 10, and the driving force transmitted to the bevel gear 9 is transmitted to the drive shaft on the bevel gear 9 side. Is transmitted. The driving force transmitted to one of the output disks 3 is applied to the ball 6 fitted in the ball groove 3b of the output disk 3.
(Shaded portion) to the eccentric disk 5, from which the ball groove 4 b of the other output disk 4
Is transmitted to the output disk 4 via the ball 6 fitted to the output disk 4. As a result, the driving force transmitted to the output disk 4 is transmitted to the drive shaft on the output disk 4 side.

Here, the operation of the differential device is defined as a case where there is no rotation difference between the drive shafts, a case where there is a rotation difference between the drive shafts, and a state where only one of the drive shafts is liable to idle. The following describes the case where the error has occurred.

First, when there is no rotation difference between the driving wheels, since the rotation of each pinion gear 10 does not occur, the one output disk 3 and the bevel gear 9 are integrated with the gear case 1 without any rotation difference. The output disk 3, the eccentric disk 5 and the other output disk 4 rotate together with the gear case 1 without rotating with each other.

Next, when a rotation difference occurs between the drive shafts, the rotation difference between the drive shafts is permitted by the following operation. In this case, since a torsional force due to the rotation difference acts on each drive shaft, each drive shaft rotates in the opposite direction to the gear case 1. At this time, when the drive shaft on the bevel gear 9 side rotates with respect to the gear case 1, each pinion gear 10 rotates and rotates one output disk 3 in the opposite direction of the bevel gear 9. When the drive shaft of the other output disk 4 rotates in the opposite direction to the bevel gear 9 with respect to the gear case 1, the other output disk 4 rotates in the same direction as the one of the output disks 3 via the eccentric disk 5. I do. That is, as shown in FIG. 7, the eccentric disk 5 between the output disks 3 and 4 is
The output disks 3, 4 rotate in the same direction as the output disks 3, 4 about a center axis L2 eccentric with respect to 1, and the rotation of each output disk 3, 4 is linked. In this case, for example, on one surface of one of the output disk 3 and the eccentric disk 5, the ball 6 of the eccentric disk 5 is fitted in the ball groove 3b of the output disk 3 by half in the circumferential direction as shown in FIG. When the output disk 3 rotates, each ball 6 is guided to the ball groove 3b while moving in the ball groove 3b of the output disk 3 by the amount of the eccentric rotation center of the eccentric disk 5. At that time, at the contact point between the ball 6 and the ball groove 3b, the ball groove 3b moves in the tangential direction D1 of a circle centered on the main axis L1.
2 moves in the tangential direction D2 of the circle centered at 2.
Such an operation is similarly performed on the other surface of the other output disk 4 and the other surface of the eccentric disk 5, and both of the output disks 3 and 4 rotate the eccentric disk 5 to rotate the output disks 3 and 4. Work smoothly with each other.

When only one of the drive shafts easily slips, for example, when the wheel of one of the drive shafts loses frictional force with the road surface, the operation of each drive shaft will be described below. Differential is limited. For example, when the drive shaft on the bevel gear 9 side has sufficiently obtained frictional force with the road surface, while the drive shaft on the other output disk 4 side is easy to idle, the drive force is applied to the gear case 1 in this state. When given, each drive shaft will be differential and one drive shaft will idle and the torque on the other drive shaft will tend to decrease. However, such a differential is limited in one output disk 3, the eccentric disk 5 and the other output disk 4. That is, when a rotational difference is generated in a state where the driving force is reliably transmitted from both drive shafts to the wheels, and the rotational force is applied to the eccentric disk 5 from both of the output disks 3 and 4, the ball 6 and the ball groove are formed. 4b are the same in the direction of force transmission, so that each output disc 3, 4
Although the eccentric disk 5 rotates easily, in the above-described case, a force for rotating the eccentric disk 5 is not applied from the output disk 4 on the drive shaft side that is about to idle.
In order to generate a differential in this state, one of the output disks 3 rotates the eccentric disk 5, and the eccentric disk 5 must rotate the other output disk 4 by this rotational force. However, one output disk 3
When only the rotational force is applied, the directions of transmission of the forces of the ball 6 and the ball groove 4b are opposite to each other, and the ball 6 of the eccentric disk 5 easily follows the movement of the ball groove 3b of the one output disk 3. When the ball groove 4b of the other output disk 4 follows the movement of the ball 6 of the eccentric disk 5, the resistance increases when the ball groove 4b of the other output disk 4 is moved.
It is very difficult to rotate. Therefore, the reaction force which the ball 6 receives from the ball groove 4b of the other output disk 4 exerts a deterrent on the rotation of the output disk 4, and the differential of each drive shaft is limited. When a rotational force P1 is input from the ball 6 to the ball groove 4b as shown in FIG. 9, a radial force P2 of the ball 6 and a force P3 in a direction perpendicular to P1 are generated in the ball groove 4b. . This P3 is a thrust load for pressing the thrust washer 4c against the gear case cover 2, thereby causing sliding friction between the thrust washer 4c and the differential cover 2, and the differential of each drive shaft is also limited by the frictional resistance. Of course, the same applies to the case where the drive shaft to be idled is opposite to that described above.

The tangent line T of the ball groove 4b contacts the ball 6 at a predetermined angle with respect to the moving direction D1 of the ball 6, as shown in FIG. Is also big. That is, as shown in FIG. 10, the moving direction of the ball 6 is the x-axis, the moving direction of the ball groove 4b is the y-axis, and the curve forming the center line of the ball groove 4b is
Is the contact angle between the ball 6 and the ball groove 4b. The magnitude of the differential limiting effect is proportional to the magnitude of the reaction force that the ball 6 receives from the ball groove 4b when the ball groove 4b attempts to follow the movement of the ball 6. That is, as shown in FIG. 10 (a), the other output disk 4 is the ball 6 of the eccentric disk 5.
Assuming that the load received from the ball 6 is W (x-axis direction), the contact angle between the ball 6 and the ball groove 4b is θ1, and the reaction force the ball 6 receives from the ball groove 4b is F1 (y-axis direction), F1 = W · tan θ1 Become. Further, as shown in FIG. 10 (b), when the contact angle between the ball 6 and the ball grooves 4 b and θ2 (> θ1), a F2 = W · tanθ2. This leads to F1 <F2,
Reaction force when the contact angle θ becomes larger ball 6 receives from the ball grooves 4 b, i.e. the differential limiting effect is can be seen that large. Therefore, by setting the magnitude of the contact angle θ arbitrarily, it is possible to obtain a necessary differential limiting effect.

As described above, according to the differential apparatus of this embodiment, during normal differential operation, the rotation difference of each drive shaft is allowed by the rotation of each pinion gear 10, and only one of the drive shafts tries to run idle. In this case, the differential of each drive shaft is limited by utilizing the mechanical characteristics of the combination of the ball 6 and the ball grooves 3b, 4b in the one output disk 3, the eccentric disk 5 and the other output disk 4. Therefore, a torque-sensitive differential limiting effect of reliable operation can be obtained, and the angle of contact between the ball 6 and the ball grooves 3b, 4b can be set arbitrarily to provide a differential as required. It is also possible to obtain a limiting effect. Further, the structure is simple and the size can be reduced, and in particular, the pinion gear 10 and the bevel gears 3a and 9 constituting the reversing mechanism can be easily manufactured by using the technology of the conventional product. It is also possible to aim.

In the above embodiment, the eccentric disk 5
Since the number of balls 6 on both sides of each output disk is the same, and the number of ball grooves 3b and 4b of each output disk 3 and 4 is also the same, the rotation ratio of each output disk 3 and 4 is the same. However, the ball 6 and the ball groove 3b,
If the number of the drive shafts 4b is made different on each drive shaft side, the rotation ratio of each output disk 3, 4 changes, and the fixed distribution ratio of the drive torque transmitted to each drive shaft changes. That is, when the rotation ratio of one output disk 3 is set to be smaller than that of the other output disk 4, the drive shaft of one output disk 3 is decelerated with respect to the other drive shaft. A larger torque is transmitted to the drive shaft on the output disk 3 side than the other drive shaft. Therefore, the drive torque distribution ratio of each drive shaft can be arbitrarily set without adding any other special parts. For example, when applied to a differential device for front and rear drive shafts of a four-wheel drive vehicle, it is extremely It is valid.

[0039]

Embodiment 2 FIGS. 11 to 16 show a second embodiment of the present invention. FIGS. 11 to 13 are sectional views of a differential device.
14 to 16 are exploded perspective views thereof. FIG.
The dashed lines in FIG. 16 to FIG. 16 indicate that they are continuous with the same numbers corresponding to the respective drawings.

This differential device includes a gear case 20 serving as an input-side rotating body, a gear case cover 21 for closing one end of the gear case 20, and an output-side rotating body disposed on the axis of the gear case 20 so as to face each other. A pair of output discs 22, a pair of eccentric discs 23 disposed on an axis eccentric with respect to the axis of the gear case 20, and a large number of balls 24 as rolling elements held in the eccentric discs 23 so as to be freely retractable. A pair of guard rings 25 covering the periphery of each eccentric disk 23, a pair of disk holders 26 rotatably holding each eccentric disk 23, and a pair of driving helical gears mounted on the rotating shaft of each eccentric disk 23. 27, and a total of four driven helical gears 28 arranged around each driven helical gear 27.

The gear case 20 is formed of a cylindrical member having one end opened, and a bearing 20a for supporting a part of one output disk 22 is provided at the other end. A flange 20b is formed in the opening of the gear case 20, and the flange 20b is provided with a number of holes 20c for bolt insertion. A hole 20d for fixing each disk holder 26 is provided on the peripheral surface of the gear case 20.

The gear case cover 21 is formed in a disk shape, and a bearing 21a for supporting a part of the other output disk 22 is provided at the center thereof. A flange 21b is formed on the periphery of the gear case cover 21, and the flange 2b is formed.
1b is provided with a number of holes 21c for bolt insertion.

Each output disk 22 is connected to each eccentric disk 23
And the helical gears 27 and 28 are opposed to each other, and a connecting portion 22a with a drive shaft (not shown) is provided on the opposite side.
Is provided. A large number of ball grooves 22b are formed on the opposing surface of each output disk 22 so as to fit with the balls 24, and each of the ball grooves 22b has a predetermined curvature curved in the same direction. In this case, each output disk 2
The two opposing surfaces have the same shape as a single product and are arranged in the opposite directions after assembly, so that the ball grooves 22b of each output disk 22 are curved in the opposite directions to the axis of each output disk 22. It will be in the state of having done. A thrust washer 22c is interposed between the rear surface of each output disk 22 and the gear case cover 21.

One end surface of each eccentric disk 23 is opposed to each output disk 22, and each output disk 2
It is arranged on an axis which is eccentric by a predetermined distance from the second axis. A large number of ball holes 23a for accommodating each ball 24 are provided through each eccentric disk 23, and the ball holes 23a are arranged at equal intervals in a line in the circumferential direction. Also,
The center of the other end surface of each eccentric disk 23 slightly protrudes in the axial direction.

Each ball 24 has an outer diameter slightly smaller than the ball hole 23a of each eccentric disk 23, and
3a is housed in a state where it can roll freely.

Each guard ring 25 has its peripheral edge bent in the radial direction, and covers the peripheral edge on one end side of each eccentric disk 23. Further, a guard wall 25a that covers the ball hole 23a of each eccentric disk 23 is provided on a half in the circumferential direction of each guard ring 25.

Each of the disk holders 26 is formed in a disk shape, and is disposed with the helical gears 27 and 28 therebetween. Each disk holder 26 is provided with a hole 26a at a position eccentric by a predetermined distance from the center. By inserting the center of the other end surface of each eccentric disk 23 into this hole 26a, each eccentric disk 26 is turned eccentrically. It is held movably. In this case, each eccentric disk 26 is
Are staggered with respect to the axis of. Further, each disk holder 26 is held at a predetermined interval by a pair of spacers 26b, and each spacer 26b is fixed by a pin 26c inserted into a hole 20d of the gear case 20, whereby
Each disk holder 26 is fixed in the gear case 20. A guide groove 26d for receiving the ball 24 of the eccentric disk 23 is provided at one end surface of each disk holder 26 at a position corresponding to the guard wall 25a of each guard ring 25, and the ball 24 of the eccentric disk 23 is secured to the guard wall 25a.
As a result, the guide groove 26d is received in the guide groove 26d by an amount protruding toward the disk holder 26 side. In this case, the portion of the ball 24 without the guard wall 25a protrudes toward each output disk 22 by the flat portion of the disk holder 26. As a result, the balls 24 of each eccentric disk 23 are fitted into the ball grooves 22b of each output disk 22 by approximately half in the circumferential direction.

The helical gears 27 on the driving side are arranged between the disk holders 26, and are fixed to the eccentric disks 23 by bolts 27a. Further, the helical gears 27 are staggered with respect to the axis of the gear case 20 like the eccentric disks 23.

The driven helical gears 28 are arranged between the disk holders 26 and rotatably supported by a shaft 28 a parallel to the rotation axis of the driven helical gear 27. Each helical gear 28 has a length extending over both the helical gears 27 on the driving side, and two helical gears are simultaneously meshed with each helical gear 27 on the driving side. In this case, since an even number of driven helical gears 28 are interposed between the helical gears 27 on the driving side, the rotations of the eccentric disks 23 are converted in directions opposite to each other. That is, reverse rotation mechanism is constituted by the helical 27,2 8.

In the above configuration, when the gear case 20 rotates around the axis by the driving force input from the outside, each eccentric disk 23 rotates around the axis of the gear case 20, and this rotational force is applied to each output disk 22. Ball groove 22b
Is transmitted to each output disk 22 by a ball 24 fitted to the output disk 22. Here, when a rotation difference occurs between the drive shafts on the output side, the ball grooves 22 of the output disks 22 roll the balls 24, and the eccentric disks 23 follow the rolling of the balls 24 and correspond to each other. It rotates in the same direction as the output disk 22. In this case, the rotation of each eccentric disk 23 is converted in the opposite direction via the helical gears 27 and 28, and each output disk 22 rotates in the opposite direction to achieve the differential of each drive shaft. At that time, each output disk 2
When a force that generates a rotation difference is applied from only one output disk 22 to the other output disk 22, the ball 24 that is the driven side during differential operation is the ball groove 22b that is the driven side.
This ball 2
4 receives a reaction force from the ball groove 22b, which acts as a resistance to limit the differential of each output disk 22. Similar to the embodiment in the case of this embodiment, the ball 2 4 ball grooves 22b
The reaction force received from the main body is mainly the force in the axial direction of each output disk 22, that is, each output disk 22 is connected to a thrust washer 22c.
Acts as a thrust load for pressing against The magnitude of the reaction force that the ball 24 receives from the ball groove 22b, that is, the magnitude of the differential limiting effect, is the same as that of the above-described embodiment.
It can be arbitrarily set by changing the size of the contact angle between the ball 4 and the ball groove 22b.

FIGS. 17 to 22 show modifications of the above-described embodiment. FIGS. 17 to 21 are sectional views of main parts of a differential device, and FIG. 22 is an exploded perspective view of the main parts. That is, in the above-described embodiment, a number of balls are used as the rolling elements, but in this modification, a number of rollers 29 are used instead of the balls. Note that the same components as those in the above embodiment are denoted by the same reference numerals.

The output disk 22 has rollers 2 described below.
9 are provided, and each roller groove 22d is formed so as to draw a curve with a predetermined curvature in the same direction.

The eccentric disk 23 is provided with a number of roller holes 23b for accommodating the respective rollers 29 at equal intervals in the circumferential direction, and the respective roller holes 23b are provided alternately and inclined in the opposite direction. In this case, the roller holes 23b are arranged on the same circumference on the surface on the output disk 22 side, and are alternately arranged on two opposite circumferences on the opposite surface of the output disk 22.

Each roller 29 is formed of a column having an outer diameter slightly smaller than the roller hole 23b of each eccentric disk 23, and is accommodated in each roller hole 23b in such a manner that it can freely come and go.

On one surface of the disk holder 26, two guide grooves 26e and 26f, which receive the roller 29 of the eccentric disk 23, are provided in the circumferential half, and the roller 29 of the eccentric disk 23 is located on the disk holder 26 side. Are received in the guide grooves 26e and 26f. In this case, the roller 29 in the portion without the guide grooves 26e and 26f protrudes toward the output disk 22 by the flat portion of the disk holder 26. As a result, the rollers 29 of the eccentric disk 23 are fitted into the roller grooves 22d of the output disk 22 by half in the circumferential direction.

With the above configuration, the same operation as the ball 24 and the ball groove 22b of the above embodiment is achieved by the rollers 29 and the roller grooves 22d. It should be noted that the use of a roller for the transmission body is the same as that of the first embodiment and the third embodiment described later.
It is also possible to apply to the fifth to fifth embodiments.

[0057]

Embodiment 3 FIGS. 23 to 30 show a third embodiment of the present invention. FIGS. 23 to 27 are sectional views of a differential device.
28 to 30 are exploded perspective views thereof. FIG. 28
30 indicate continuous lines with the same numbers corresponding to the respective figures.

This differential device includes a gear case 30 serving as an input-side rotating body, a gear case cover 31 closing one end of the gear case 30, a center disk 32 serving as a driven rotating body disposed in the center of the gear case 30, and A pair of eccentric disks 33 arranged on both sides of the center disk 32
A large number of balls 34 as rolling elements supported on each eccentric disk 33 so as to be freely retractable; a pair of guard rings 35 covering the periphery of each eccentric disk 33;
A pair of disk holders 36 that rotatably support 3;
A pair of eccentric gears 37 attached to the rotation shafts of the respective eccentric disks 33, a pair of output gears 38 arranged coaxially with the respective eccentric gears 37 in between, and a pair of eccentric gears 37 and the respective output gears 38; It comprises a total of six helical gears 39 arranged on the periphery, and each drive shaft (not shown) is connected to each output gear 38.

The gear case 30 is formed of a cylindrical member having one end opened, and a bearing 30a through which a part of one output gear 38 penetrates is provided at the other end. A flange 30b is formed in the opening of the gear case 30, and the flange 30b is provided with a number of holes 30c for bolt insertion. The other end of the gear case 30 is provided with holes 30d for fixing one disk holder 36 at a total of two places.

The gear case cover 31 is formed in a disc shape, and a bearing 31a through which a part of the other output gear 38 penetrates is provided at the center. Gear case cover 31
A flange 31b is formed on the periphery of the
Are provided with a number of holes 31c for bolt insertion.
The gear case cover 31 has holes 31d for fixing the other disk holder 36 at a total of two places.

The center disk 32 is slidably supported on the inner surface of the gear case 30, and has a large number of ball grooves 32a on both surfaces for fitting with respective balls 34 described later. Each ball groove 32a is formed so as to draw a curve with a predetermined curvature in the same direction, and when they are overlapped in the axial direction, they curve in opposite directions.

Each eccentric disk 33 is a center disk 32
The surfaces facing each other are formed smoothly, and these surfaces are slidably opposed to both surfaces of the center disk 32.
The opposite surface of each eccentric disk has a central portion formed with a small diameter, and this portion is supported by the disk holder 36, so that it is eccentric by a predetermined distance to the opposite side of the center axis (main axis) of the center disk 32. Held in state. On the surface facing the center disk 32, a number of ball holes 33a for accommodating the respective balls 34 are provided at equal intervals in the circumferential direction, and the depth of each of the ball holes 33a is
4 is formed slightly smaller than the outer diameter.

Each ball 34 has an outer diameter slightly smaller than the ball hole 33a of each eccentric disk 33,
3a is housed in a state where it can freely appear and disappear.

Each guard ring 35 is formed in an L-shaped cross section, and covers the periphery of one end of each eccentric disk 33. A guard wall 35a that covers the ball hole 33a of the eccentric disk 33 is provided in a circumferential half of each guard ring 35, and the guard wall 35a prevents the half ball 34 in the circumferential direction from protruding from the ball hole 33a. I have. Also, each guard ring 35 is provided with a disk holder 3 described later by projecting pieces 35b provided at a total of two places.
6 fixed.

Each disk holder 36 is formed in a disk shape, and rotatably supports the eccentric disk 33 by inserting a small diameter portion of the eccentric disk 33 into a circular hole 36a. The outer peripheral surface of each disk holder 36 is formed around the main shaft, while the hole 36a for supporting the eccentric disk 33 is formed around an axis that is eccentric by a predetermined distance from the main shaft. Each disk holder 36 is held at a predetermined interval by a pair of spacers 36b.
6b is the hole 3 of the gear case 30 and the gear case cover 31
Each disk holder 36 is fixed in the gear case 30 by fixing with the pins 36c inserted into 0d and 31d. Further, on one surface of the disk holder 3 6 provided at a position where the guide groove 36d for receiving the ball 34 of the eccentric disk 33 corresponds to the guard wall 35a of the guard ring 35, the ball 34 of the eccentric disk 33 is guard wall 3
5a allows the guide groove 36d to receive the portion protruding toward the disk holder 36 side. In this case, the portion of the ball 34 without the guard wall 35a protrudes toward the center disk 32 by the flat portion of the disk holder 36. Thereby, the ball 3 of each eccentric disk 33
4 are fitted into the ball grooves 32a of the center disk 32 by half in the circumferential direction.

Each eccentric gear 37 is arranged outside each eccentric disk 33, and is fixed to each eccentric disk 33 by a bolt 37a. Each eccentric gear 37, like each eccentric disk 33, is eccentric to the opposite side with respect to the main shaft.

Each output gear 38 is formed with a gear 38a at one end. One gear 38a faces one eccentric gear 37, and the other gear 38a faces the other eccentric gear 37. The other end of each output gear 38 is provided with a coupling portion 38b for connecting to each drive shaft. Each coupling portion 38b is provided with bearings 30a, 31 of the gear case 30 and the gear case cover 31.
a.

Each helical gear 39 has a length extending over both the eccentric gear 37 and the output gear 38, and meshes with each eccentric gear 37. On one eccentric gear 37 and output gear 38 side, a total of four helical gears 39 are arranged,
These are meshed with each other as a pair. Further, a total of two helical gears 39 are individually arranged on the other eccentric gear 37 and the output gear 38 side. Each helical gear 39 is inserted into a shaft 39a, and each shaft 3
9a has one disk holder 36 and the gear case 3
0 and between the other disk holder 36 and the gear case cover 31.

In the differential device configured as described above, when the torque of the engine is transmitted to the gear case 30, the gear case 30 rotates about the axis, and each disk holder 36 is integrated with the gear case 30. Rotate. Thereby, the driving force transmitted to each disk holder 36 is distributed to each eccentric disk 33, and the driving force transmitted to each eccentric disk 33 is transmitted to the drive shaft of each output gear 38 via the eccentric gear 37 and the helical gear 39. Is transmitted.

In the above configuration, when the gear case 30 rotates around the axis by an external driving force, each eccentric disk 33 rotates around the axis of the gear case 30, and this rotational force is applied to each eccentric gear 37 and each The power is transmitted to each output gear 38 via the helical gear 39. Here, when a rotation difference occurs between the drive shafts on the output side, the eccentric disks 33 rotate in the same direction about the axis eccentric with respect to the axis of the gear case 30 and are held by the eccentric disks 33. Ball 34 is formed in ball groove 32a of center disk 32.
, The center disk 32 rotates in the same direction as each eccentric disk 33 following the rolling of the ball 34. In this case, the rotation of one output gear 38 is converted in the opposite direction via an even number of helical gears 39, and each output gear 38 rotates in the opposite direction to achieve the differential of each drive shaft. At this time, when a force that causes a rotation difference is applied to each output gear 38 from only one of the output gears 38, the ball groove 32a, which is the driven side at the time of differential operation, causes the ball 34, which is the driven side, to move on its own in the center disk 32. The ball groove 32a receives a reaction force from the ball 34, and this acts as a resistance to limit the differential of each output gear 38.

[0071]

Embodiment 4 FIGS. 31 to 37 show a fourth embodiment of the present invention. FIGS. 31 to 34 are sectional views of a differential device.
35 to 37 are exploded perspective views thereof. FIG. 35
37 indicate that they are continuous with the same numbers corresponding to the respective figures.

The differential device includes a gear case 40 forming an input-side rotating body, a gear case cover 41 closing one end of the gear case 40, and a pair of output disks arranged concentrically in the gear case 40 so as to face each other. 42, 43
And an eccentric disk 44 disposed between the output disks 42 and 43, a number of balls 45 as rolling elements supported by the output disks 42 and 43 so as to be freely retractable, and peripheral edges of the output disks 42 and 43. Two guard rings 4 to cover
6, a disk holder 47 that rotatably supports the eccentric disk 44, a fixed disk 48 that rotatably supports one output disk 42, and a main shaft that is coaxially arranged to face the one output disk 42. A gear 49, a ring gear 50 that covers the main shaft gear 49 at intervals in the circumferential direction,
Total 4 arranged between the main shaft gear 49 and the ring gear 50
Planetary gears 51 and each planetary gear 51
And a planetary carrier 52 that supports
Each drive shaft (not shown) is coupled to one output disk 42 and main shaft gear 49, respectively.

The gear case 40 is formed of a cylindrical member having one end opened, and a through portion 40a through which one drive shaft passes is provided at the other end. A flange 40b is formed in the opening of the gear case 40, and the flange 40b is provided with a number of holes 40c for bolt insertion. The other end of the gear case 40 is provided with a hole 40d for fixing the ring gear 50.

The gear case cover 41 is formed in a disk shape, and a bearing 41a through which a part of the other output disk 43 penetrates is provided at the center. A flange 41 b is formed on the periphery of the gear case cover 41, and the flange 4 b
1b is provided with a number of holes 41c for bolt insertion. On the inner surface of the gear case cover 41, a guide groove 41d for receiving the ball 45 of the other output disk 43 is provided in a half in the circumferential direction.
5 is received in the guide groove 41d by an amount protruding toward the gear case cover 41 by a guard wall 46a described later. In this case, the ball 45 in the portion without the guard wall 46a protrudes toward the other eccentric disk 44 by the flat portion of the gear case cover 41. This allows
The ball 45 of the other output disk 43 fits into a ball groove 44b of an eccentric disk 44, which will be described later, by half in the circumferential direction. The gear case cover 41 has the disc holder 4
A hole 41e for fixing the nozzle 7 is provided.

One output disk 42 is the eccentric disk 4
The facing surfaces while being smoothly formed with 4, the opposite side is formed a center diameter and has a hole 42a for connecting the planetary carrier 5 2. On the surface facing the eccentric disk 44, a number of ball holes 42b for accommodating the respective balls 45 are provided at equal intervals in the circumferential direction, and the depth of each of the ball holes 42b is slightly smaller than the outer diameter of each of the balls 45. It is formed small.

The other output disk 43 is the eccentric disk 4
4, and a coupling portion 43a with the drive shaft is provided on the opposite side. Also,
A large number of ball holes 43b for accommodating each ball 45 are provided at equal intervals in the circumferential direction on the surface facing the eccentric disk 44, as described above, and the depth of each ball hole 43b is
Is formed slightly smaller than the outer diameter of.

The eccentric disk 44 is composed of a pair of disk-shaped members divided in the axial direction, and these are connected to each other by pins 44a. Both surfaces of the eccentric disk 44 are formed to be smooth, respectively, and these surfaces are
2, 43 are slidably opposed. Eccentric disk 44
The central portion in the axial direction is formed to have a small diameter, and this portion is supported by the disk holder 47, so that the output disks 42 and 43 are held eccentric by a predetermined distance from the central axis (main axis). Also, on both surfaces of the eccentric disk 44, a number of ball grooves 44b fitted with the respective balls 45 are provided.
Are provided, and each ball groove 44b is formed so as to draw a curve with a predetermined curvature in the same direction. in this case,
The ball grooves 44b are curved in opposite directions when overlapped in the axial direction.

Each ball 45 is connected to each output disk 42, 43
Ball hole 42 b, than 43 b has a smaller outer diameter slightly are accommodated in a state that can be infested freely to each ball holes 42 b, 43 b.

Each guard ring 46 is formed in an L-shaped cross section, and covers the periphery of each of the output disks 42 and 43, respectively. Ball hole 42 b, a guard wall 46a covering the 43 b in the circumferential direction is halved output disks 42, 43 are provided for each of the guard ring 46, the ball hole 42 a ball 45 in the circumferential direction one half by the guard wall 46a b, so as not to protrude from the 43 b. In addition, each guard ring 46
The gear case cover is provided by a protruding piece 46b provided at the peripheral end.
-41 and a fixed disk 48 , respectively .

The disk holder 47 has a circular hole 47a, and the eccentric disk 44 is rotatably supported by inserting a small diameter portion of the eccentric disk 44 into the hole 47a. The outer peripheral surface of the disk holder 47 is formed around the main shaft, while the hole 47a for supporting the eccentric disk 44 is formed around an axis that is eccentric by a predetermined distance from the main shaft. The disc holder 47 has a hole 4 provided at one end thereof.
The pin 47c is fixed in the gear case 40 by inserting a pin 47c into the hole 41e of the gear case cover 7b. The other end of the disc holder 47 is provided with a hole 47d for fixing the fixed disc 48.

The fixed disk 48 has a circular hole 48a in the center.
The output disk 42 is rotatably supported by inserting the small diameter portion of one output disk 42 into the hole 48a. The fixed disk 48 is provided with a pin 4 in a hole 48b provided on the peripheral edge side and a hole 47d of the disk holder 47.
8c is fixed to the disc holder 47 by inserting it.

The main shaft gear 49 is a planetary carrier 52
And a coupling portion 49a with the drive shaft is provided at the center thereof.

The outer peripheral surface of the ring gear 50 is
Are formed along the inner surface of the inner ring, and an inner gear is provided on the inner peripheral surface. The ring gear 50 is fixed in the gear case 40 by inserting a pin 50 a fitted into a concave portion on the outer peripheral surface into a hole 40 d of the gear case 40.

Each of the planetary gears 51 is meshed with each other as a pair, and one of the planetary gears 51 meshes with the main shaft gear 49 and the other planetary gear 51 meshes with the ring gear 50. .

The planetary carrier 52 is composed of a total of two disk-shaped members disposed at both ends of each planetary gear 51, and supports each planetary gear 51 rotatably. The planetary carrier 52 is fixed to the output disk 42 by inserting a pin 52b into a hole 52a provided in one disk and a hole 42a of one output disk 42.

In the above configuration, when the gear case 40 rotates around the axis by an external driving force, the eccentric disk 44 rotates about the axis of the gear case 40, and this rotational force is applied to the output disks 42 and 43. The light is transmitted to each of the output disks 42 and 43 via a ball groove 44b fitted to the ball 45. Here, when a rotation difference occurs between the drive shafts on the output side, the balls 45 of the output disks 42 and 43 roll along the ball grooves 44b, and the eccentric disks 44
5 and rotates in the same direction as the output disks 42 and 43. In this case, the rotation of one output disk 42 is converted in the opposite direction via each planetary gear 51, and each output disk 42, 43 rotates in the same direction as each other, thereby achieving the differential of each drive shaft. At this time, when a force causing a rotation difference between the output disks 42, 43 is applied from only one of the output disks 42, 43, the eccentric disk 44
In this case, the ball groove 44b on the driven side at the time of differential attempts to make the ball 45 on the driven side follow its own movement.
The ball groove 44b receives a reaction force from the ball 45, which acts as a resistance, thereby limiting the differential between the output disks 42 and 43.

[0087]

Embodiment 5 FIG. 38 through FIG. 44 shows a fifth embodiment of the present invention, FIG. 38 乃 optimum view 41 is a sectional view of a differential device,
42 to 44 are exploded perspective views thereof. Note that FIG.
44 through FIG. 44 indicate that they are continuous with the same numbers corresponding to the respective figures.

This differential device includes a gear case 60 serving as an input-side rotating body, a gear case cover 61 closing one end of the gear case 60, and a pair of output disks arranged concentrically in the gear case 60 so as to face each other. 62, 63
An eccentric disk 64 disposed between the output disks 62 and 63, a number of balls 65 as rolling elements supported by the eccentric disk 64, and a pair of guard rings 66 covering the peripheral edge of the eccentric disk 64; A disk holder 67 that rotatably supports the eccentric disk 64,
Each drive shaft (not shown) is connected to each output disk 62, 6
3.

The gear case 60 is formed of a cylindrical member having one end opened, and a bearing 60a through which one drive shaft passes is provided at the other end. A flange 60b is formed at the opening of the gear case 60, and the flange 60b is provided with a number of holes 60c for bolt insertion. Also,
A hole 60 d for fixing the disk holder 67 is provided on the peripheral surface of the gear case 60.

The gear case cover 61 is formed in a disk shape, and a bearing 61a through which a part of the other output disk 63 penetrates is provided at the center. A flange 61b is formed on the periphery of the gear case cover 61,
1b is provided with a number of holes 61c for bolt insertion.

Each of the output disks 62 and 63 has a smooth surface facing the eccentric disk 64, and coupling portions 62a and 63a with the respective drive shafts are provided on the opposite side. Further, a large number of ball grooves 62 to be fitted with the respective balls 65 described later are provided on the surface facing the eccentric disk 64.
b and 63b are provided, and each of the ball grooves 62b is formed so as to draw a curve with a predetermined curvature in the same direction. On the other hand, each of the other ball grooves 63b is formed so as to draw a curve with a predetermined curvature in the same direction as each other, but the length thereof is longer than that of each one of the ball grooves 62b. Are formed to curve in the opposite direction. Each of the output disks 62 and 63 is
63a is inserted into the bearings 60a, 61a of the gear case 60 and the gear case cover 61, and thrust washers 62c, 63c are interposed between the rear surface thereof and the gear case 60 or the gear case cover 61.

The eccentric disk 64 has smooth surfaces on both sides, and these surfaces are slidably opposed to the output disks 62 and 63. Further, the eccentric disk 64 is formed of a disk-shaped member divided in the axial direction, and these are connected to each other by bolts 64a. Eccentric disk 6
The central portion in the axial direction of 4 is formed to have a small diameter, and this portion is supported by the disk holder 67, so that the output disks 62 and 63 are held eccentrically by a predetermined distance from the central axis (main axis). The eccentric disk 6
A large number of ball holes 64b for accommodating each ball 65 are provided at equal intervals in the circumferential direction on both surfaces of the balls 2 and 63, and the depth of each ball hole 64b is formed to be slightly smaller than the outer diameter of the ball 65. .

Each ball 65 has an outer diameter slightly smaller than the ball hole 64b of the eccentric disk 64.
b.

Each guard ring 66 has an L-shaped cross section and covers the periphery of the eccentric disk 64. An eccentric disk 64 is provided on the circumferential half of each guard ring 66.
A guard wall 66a is provided to cover the ball hole 64b, and the guard wall 66a prevents half of the ball 65 in the circumferential direction from protruding from the ball hole 64b. Also,
Each guard ring 66 is fixed to a disk holder 67 described later by a protruding piece 66b provided at a peripheral end.

The disk holder 67 has a circular hole 67a, and the eccentric disk 64 is rotatably supported by inserting a small diameter portion of the eccentric disk 64 into the hole 67a. The outer peripheral surface of the disk holder 67 is formed around the main shaft, but the hole 67a for supporting the eccentric disk 64 is formed around an axis that is eccentric by a predetermined distance from the main shaft. The disk holder 67 is fixed in the gear case 60 by a spacer 67b that matches a part of the disk holder 67 in the circumferential direction.
The spacer 67b is fixed by a pin 67c inserted into the hole 60d of the gear case 60. Guide grooves 67d for receiving the balls 65 of the eccentric disk 64 are provided on both sides of the disk holder 67 at positions corresponding to the guard walls 66a of the guard rings 66, respectively.
The ball 65 is received in the guide groove 67d by an amount protruding toward the disk holder 67 by the guard wall 66a. In this case, the portion of the ball 65 without the guard wall 66a protrudes toward each of the output disks 62 and 63 by the flat portion of the disk holder 67. This allows
The balls 65 arranged on both surfaces of the eccentric disk 64 fit into the ball grooves 62b and 63b of the output disks 62 and 63, respectively, in half in the circumferential direction.

In the above configuration, when the gear case 60 rotates around the axis by an external driving force, the eccentric disk 64 rotates about the axis of the gear case 60, and this rotational force is applied to each of the output disks 62 and 63. Ball groove 62b, 6
3b, each output disk 6 is connected via a ball 65.
2, 63. Here, when a rotation difference occurs between the drive shafts on the output side, the ball grooves 62b, 63b of the output disks 62, 63 roll the ball 65, and the eccentric disk 64 follows the rolling of the ball 65, and Rotate in the same direction as the output disk 62. In this case, the ball grooves 62b, 63b of the other output disk 63 are
Therefore, the output disks 62 and 63 rotate in directions opposite to each other, thereby achieving a differential between the drive shafts. At that time, each output disk 6
When a force that generates a rotation difference is applied only from one of the output disks 62 to the second and third output disks 63, the ball 65, which is the driven side during differential operation, follows the ball groove 63b, which is the driven side, during its differential movement. The ball 65 receives a reaction force from the ball groove 63b to act as a resistance, and this acts as a resistance to limit the differential between the output disks 62 and 63.

In the case of this embodiment, each output disk 62, 6
The output discs 62, 63 are rotated in opposite directions by providing the third ball grooves 62b, 63b in curved directions opposite to each other, so that the components as a reversing mechanism as in other embodiments are provided. Is not required separately.

[0098]

Sixth Embodiment FIGS. 45 to 49 show a sixth embodiment of the present invention. FIGS. 45 to 47 are side sectional views of a differential device, and FIGS. 48 and 49 are exploded perspective views of the differential device. FIG.
Note that the dashed line in FIGS. 48 and 49 indicates that they are consecutive with the same number corresponding to each figure.

This differential device includes a gear case 70 serving as an input-side rotating body, a gear case cover 71 for closing one end of the gear case 70, a ring gear 72 mounted on the outer periphery of the gear case 70, and a gear case 70. A pair of output discs 73 and 74 as output-side rotating bodies arranged opposite to each other, an eccentric disc 75 arranged on an axis eccentric with respect to the axis of the gear case 70, and an eccentric disc 75 which can be freely retracted. A number of balls 76 held,
A pair of disk holders 77 rotatably holding an eccentric disk 75, one bevel gear 73a integrally provided on one output disk 73, and one bevel gear 73
The other bevel gear 78 is disposed on the axis of the gear case 70 so as to oppose a, and a total of four pinion gears 79 are interposed between the bevel gears 73a and 78.

The gear case 70 is formed of a cylindrical member having one end opened, and a bearing 70a for supporting a bevel gear 78 is provided at the other end. A flange 70b is formed in the opening of the gear case 70, and the flange 70b is provided with a number of holes 70c for bolt insertion. Also,
A receiving groove 70 d for supporting the pinion gear 79 is provided inside the gear case 70.

The gear case cover 71 is formed in a disk shape, and a bearing 71a for supporting a part of the output disk 74 is provided at the center thereof. A flange 71b is formed around the periphery of the gear case cover 71, and the flange 71b is provided with a number of holes 71c for bolt insertion.

The ring gear 72 has one end formed by a gear, and has an inner diameter slightly larger than the outer diameter of the gear case 70. A screw hole 72a is provided in the other end surface of the ring gear 72, and a bolt 72b inserted through holes 70c, 71c of the gear case 70 and the gear case cover 71.
Is screwed into the screw hole 72a of the ring gear 72, whereby the gear case 70, the gear case cover 71, and the ring gear 72 are integrally connected.

One output disk 73 has one end face facing the eccentric disk 75, and a bevel gear 73a is integrally provided on the opposite side. On one end surface of the output disk 73, a number of ball grooves 73 fitted with the respective balls 76 are provided.
b is formed, and each ball groove 73b draws a curve of a predetermined curvature curved in the same direction. The output disk 7
A thrust washer 73c is interposed between the peripheral edge of the gear 3 and a step in the gear case 70.

The other output disk 74 has one end face facing the eccentric disk 75, and the other side is not shown.
Connecting portions 7 4 a is provided to have connected to one of the drive shaft. A plurality of ball grooves 74b are formed on one end surface of the output disk 74 so as to fit with the respective balls 76.
4 b is similar to the one output disk 73 depicts a curve of a predetermined curvature which is curved in the same direction. In this case, the opposing surfaces of the output disks 73 and 74 have the same shape as a single product and are arranged in the opposite directions after assembly, so that the ball grooves 73b and 74 of the output disks 73 and 74 are provided.
b is in a state of being curved in directions opposite to each other with respect to the axis of each of the output disks 73 and 74. Also, the output disk 74
A thrust washer 74c is interposed between the rear surface of the gear case and the gear case cover 71.

The eccentric disk 75 has its both end faces opposed to the output disks 73 and 74, respectively, and is disposed on an axis which is eccentric by a predetermined distance from the axis of each of the output disks 73 and 74. A large number of ball holes 75a for accommodating the respective balls 76 are provided through the eccentric disk 75, and the respective ball holes 75a are arranged at equal intervals in a line in the circumferential direction. The center of both end faces of the eccentric disk 75 slightly protrudes in the axial direction.

Each ball 76 has an outer diameter slightly smaller than the ball hole 75a of the eccentric disk 75.
a so as to be freely rolled.

Each disk holder 77 is formed in a disk shape and is fixed in the gear case 70, respectively. Each disc holder 77 is provided with a hole 77a at a position eccentric by a predetermined distance from the center, and the center of both end faces of the eccentric disc 75 is inserted into this hole 77a, so that the eccentric disc 75 is rotatable in an eccentric state. Is held. Each of the disk holders 77 is provided with a ball guide 77b extending circumferentially along each of the ball holes 75a of the eccentric disk 75. The ball guide 77b includes a first guide portion 77c that can penetrate the ball 76, and a ball guide 77b. A second guide 77d for holding the ball 76 in the neutral position, and the ball 76
5 and a third guide portion 77e which is displaced in the axial direction. The first guide portion 77c is formed in a substantially half range in the circumferential direction, and the first guide portion 77c of one disk holder 77 is connected to the second guide portion 77 of the other disk holder 77.
d and the third guide portion 77e. That is, on one end face of the eccentric disk 75,
The ball 76 located in the third guide portion 77e of the one disk holder 77 projects toward the one output disk 73 via the first guide portion 77c of the other disk holder 77, and fits into the ball groove 73b of the output disk 73. I do. On the other end surface of the eccentric disk 75, a ball 76 located in the third guide portion 77e of the other disk holder 77 is provided.
Project toward the other output disk 74 via the first guide portion 77c of one disk holder 77, and the output disk 7
4 is fitted into the ball groove 74b.

The bevel gear 78 has a connecting portion 78a for connecting to the other of the drive shafts ( not shown ), and is rotatably supported by a bearing 70a of the gear case 70. A washer 7 is provided between the rear surface of the bevel gear 78 and the gear case 70.
8b is interposed.

Each pinion gear 79 is rotatably supported by a total of four support shafts 79a orthogonal to the axis of the gear case 70, and transmits the rotational force of each bevel gear 73a, 78 to each other. Each support shaft 79a is received in a receiving groove 70d of the gear case 70 via a washer 79b, and is fixed in the gear case 1. In this case, the rotation of one output disk 73 is converted in the opposite direction by the rotation of each pinion gear 79. That is, the bevel gears 73a and 78 and the pinion gears 79 constitute a reverse rotation mechanism.

In the above configuration, when the gear case 70 rotates around the axis by an external driving force, the eccentric disk 75 rotates about the axis of the gear case 70, and this rotational force is applied to each of the output disks 73 and 74. Ball groove 73b, 7
Each output disk 7 is connected to a ball 76 via a ball 76 fitted to the output disk 7b.
3, 74. Here, when a rotation difference occurs between the drive shafts on the output side, the rotation of one output disk 73 is converted in the opposite direction by the rotation of each pinion gear 79, and each output disk 73, 74 is centered on the rotation shaft of the gear case 70. In this way, the drive shafts are rotated in the same direction to achieve the differential of each drive shaft. At this time, when a force that causes a rotation difference between the output disks 73 and 74 is applied from only one of the output disks 73,
On the other output disk 74, the ball 76, which is the driven side at the time of differential operation, tries to make the ball groove 73 b, which is the driven side, follow its own movement.
b receives a reaction force, which acts as a resistance to limit the differential of each output side rotating body.

[0111]

As described above, claims 1 and 2,
According to the differentials 3, 4, and 5, an extremely stable differential limiting effect of a torque-sensitive type can be obtained as compared with a conventional differential using a rotational speed-sensitive viscous coupling or the like. At the same time, it is easier to manufacture and has fewer parts than those using a conventional worm gear, which is extremely advantageous for improving productivity and miniaturizing. In addition, by arbitrarily setting the contact angle between the rolling element and the groove, a necessary differential limiting effect can be easily obtained. Furthermore, since the drive torque distribution ratio of each drive shaft can be set arbitrarily without adding other special parts, for example, when applied to a differential device for a front-rear drive shaft of a four-wheel drive vehicle, Is extremely effective.

[Brief description of the drawings]

FIG. 1 is a side sectional view of a differential device according to a first embodiment of the present invention.

FIG. 2 is a sectional view taken along line AA of FIG. 1;

FIG. 3 is a sectional view taken along line BB of FIG. 1;

FIG. 4 is an exploded perspective view of the differential device.

FIG. 5 is an exploded perspective view of the differential device.

FIG. 6 is a schematic configuration diagram of a differential device.

FIG. 7 is an explanatory diagram of an operation of an output disk and an eccentric disk.

FIG. 8 is a diagram illustrating the operation of a ball and a ball groove.

FIG. 9 is an explanatory diagram of an action of a force applied from a ball to a ball groove.

FIG. 10 is a diagram for explaining a differential limiting effect due to a difference in contact angle.

FIG. 11 is a side sectional view of a differential device according to a second embodiment of the present invention.

12 is a sectional view taken along line AA of FIG. 11;

13 is a sectional view taken along line BB of FIG. 11;

FIG. 14 is an exploded perspective view of the differential device.

FIG. 15 is an exploded perspective view of the differential device.

FIG. 16 is an exploded perspective view of the differential device.

FIG. 17 is a partial side sectional view of a differential device showing a modification of the second embodiment.

18 is a sectional view taken along line AA of FIG. 17;

19 is a sectional view taken along line BB of FIG. 17;

20 is a sectional view taken along line CC of FIG. 17;

21 is a cross-sectional view taken along line DD of FIG. 17;

FIG. 22 is a partially exploded perspective view of the differential device.

FIG. 23 is a side sectional view of a differential gear according to a third embodiment of the present invention.

24 is a sectional view taken along line AA of FIG. 23;

FIG. 25 is a sectional view taken along line BB of FIG. 23;

FIG. 26 is a sectional view taken along line CC of FIG. 23;

FIG. 27 is a cross-sectional view taken along line DD of FIG. 23;

FIG. 28 is an exploded perspective view of the differential device.

FIG. 29 is an exploded perspective view of the differential device.

FIG. 30 is an exploded perspective view of the differential device.

FIG. 31 is a side sectional view of a differential gear according to a fourth embodiment of the present invention.

FIG. 32 is a sectional view taken along line AA of FIG. 31;

FIG. 33 is a sectional view taken along line BB of FIG. 31;

34 is a sectional view taken along line CC of FIG. 31;

FIG. 35 is an exploded perspective view of the differential device.

FIG. 36 is an exploded perspective view of the differential device.

FIG. 37 is an exploded perspective view of the differential device.

FIG. 38 is a side sectional view of a differential gear according to a fifth embodiment of the present invention.

39 is a cross-sectional view taken along line AA of FIG. 38.

40 is a sectional view taken along line BB of FIG. 38;

41 is a sectional view taken along line CC of FIG. 38;

FIG. 42 is an exploded perspective view of a differential device.

FIG. 43 is an exploded perspective view of the differential device.

FIG. 44 is an exploded perspective view of the differential device.

FIG. 45 is a side sectional view of a differential gear according to a sixth embodiment of the present invention.

46 is a cross-sectional view taken along line AA of FIG. 45.

FIG. 47 is a sectional view taken along line BB of FIG. 45;

FIG. 48 is an exploded perspective view of the differential device.

FIG. 49 is an exploded perspective view of a differential device.

[Explanation of symbols]

1, 20, 30, 40, 60 ... gear case, 3, 4, 2
2, 42, 43, 62, 63 ... output disk, 5, 2
3, 33, 44, 64: eccentric disk, 32: center disk, 6, 24, 34, 45, 65: ball, 3b,
4b, 22b, 32a, 44b, 62b, 63b: ball groove, 29: roller, 22d: roller groove.

──────────────────────────────────────────────────続 き Continued on front page (58) Field surveyed (Int.Cl. ⁶ , DB name) F16H 48/20

Claims (5)

(57) [Claims] An input-side rotator that rotates around an axis by a driving force input from the outside, and an input-side rotator that is rotatable about an axis eccentric with respect to the axis of the input-side rotator. Eccentric rotator, a pair of output rotators disposed on the axis of the input rotator facing both end surfaces of the eccentric rotator, and circumferentially equally spaced at both end surfaces of the eccentric rotator A large number of rolling elements held in the large number of holes provided in the eccentric rotating body and a part of the rolling elements held by the eccentric rotating body project from both end surfaces of the eccentric rotating body at predetermined positions in the circumferential direction of the eccentric rotating body. And a reversing mechanism for converting the rotation of one output side rotating body in the opposite direction and transmitting the rotation to the outside. Each output side rotating body is eccentric when each output side rotating body rotates in the same direction. Guide the rolling elements protruding from both end faces of the rotating A differential device comprising a plurality of grooves for rotating in a direction. 2. An input-side rotator that rotates around an axis by a driving force input from the outside, and an input-side rotator that is rotatable about an axis that is eccentric with respect to the axis of the input-side rotator. A pair of eccentric rotators held on the eccentric rotator, and a pair of output rotators arranged on the axis of the input rotator facing one end face of each eccentric rotator; A large number of rolling elements held in a large number of holes provided at equal intervals in the circumferential direction on one end surface of the eccentric rotary body, and a number of rolling elements held by each eccentric rotary body are partially replaced by an eccentric rotary body. A guide portion that protrudes from one end surface of the eccentric rotator at a predetermined position in the circumferential direction, and a reversing mechanism that converts the rotation of each eccentric rotator into a direction opposite to each other, wherein each output rotator includes Guides rolling elements protruding from one end face of each eccentric rotor when rotating in opposite directions A plurality of grooves for rotating the respective eccentric rotary members in directions opposite to each other. 3. An input-side rotator rotating around an axis by a driving force input from the outside, and a driven rotation held by the input-side rotator so as to be rotatable about the axis of the input-side rotator. A pair of eccentric rotators each arranged with one end face facing both ends of the driven rotator in a rotatable state about an axis eccentric to the axis of the input-side rotator; A pair of output-side rotators arranged on the axis of the input-side rotator with the rotator interposed therebetween, and a large number of holes provided at equal intervals in the circumferential direction on one end surface of each eccentric rotator so as to be freely retractable. A plurality of rolling elements held, a guide portion for projecting a part of the rolling elements held by each eccentric rotary body from one end surface of the eccentric rotary body at a predetermined position in a circumferential direction of the eccentric rotary body; Rotation is converted to forward for one output rotator and reverse for the other output rotator A reverse rotation mechanism that transmits the driven rotator to the driven rotator in a predetermined direction by guiding the rolling members projecting from both end surfaces of the eccentric rotator when the eccentric rotators rotate in the same direction. A differential device comprising a number of grooves to be rotated. 4. An input-side rotator that rotates around an axis by a driving force input from the outside, and an input-side rotator that is rotatable about an axis that is eccentric with respect to the axis of the input-side rotator. An eccentric rotator held by the eccentric rotator, a pair of output rotators arranged on the axis of the input rotator with one end face facing both end faces of the eccentric rotator, and one end face of each output rotator A large number of rolling elements held in a large number of holes provided at equal intervals in the circumferential direction so as to be able to protrude and retract, and a part of the rolling elements held by each output-side rotating body are moved at predetermined positions in the circumferential direction of the eccentric rotating body. A guide portion projecting from both end surfaces of the eccentric rotator; and a reversing mechanism for converting the rotation of one output-side rotator into a reverse direction and transmitting the rotation to the outside. Guides rolling elements protruding from one end face of each output side rotating body when they rotate in the same direction. A plurality of grooves for rotating the eccentric rotator in a predetermined direction. 5. An input-side rotator that rotates around an axis by a driving force input from the outside, and an input-side rotator that is rotatable about an axis that is eccentric with respect to the axis of the input-side rotator. An eccentric rotator held on the eccentric rotator, a pair of output rotators disposed on the axis of the input rotator with one end face facing each end face of the eccentric rotator, A large number of rolling elements held in a large number of holes provided at equal intervals in the direction, and a part of the rolling elements held by the eccentric rotator, and a part of the eccentric rotator A guide portion that protrudes from both end surfaces. Each output-side rotator guides a rolling element protruding from one end surface of each output-side rotator when each output-side rotator rotates in a direction opposite to each other. A differential device comprising a plurality of grooves for rotating a body in a predetermined direction.