JP2980532B2 - 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 or front and rear drive wheels of a motor vehicle, and more particularly to a differential device having a differential limiting function.

[0002]

2. Description of the Related Art A differential device for an automobile is a device that allows a difference in rotation between left and right drive wheels when the vehicle travels on a curve or a difference in rotation between front and rear drive wheels in a four-wheel drive vehicle. A pinion gear is interposed between a pair of bevel gears connected to the shaft, and when a rotational force is applied to the shaft of the pinion gear from the outside, the pinion gear rotates on a differential basis to allow a rotation difference between the output shafts. Are common.

[0003] However, only one of the drive wheels has snow or sand.
When riding on a road surface with an extremely low coefficient of friction, one of the wheels spins due to the differential and the entire driving force is lost,
It was easy to fall into a state where you could not escape from the place. In addition, even when the load on the inner wheels is extremely reduced by centrifugal force when traveling at high speed on a curve, the driving force for traveling at high speed on the curve is likely to be lost because the wheels with reduced load run idle. There are drawbacks.

[0004] To compensate for such a drawback, there is a type provided with a differential limiting mechanism such as a clutch disk crimping type. However, even when one of the driving wheels is not grounded, it is used.
In many cases, a preload is applied to the clutch disc in order to obtain the driving force. As a result, in this type, each driving wheel is restrained with each other even during non-driving and when decelerating where no driving force is input from the engine side. There has been a problem in combination with a device that requires independence in rotation of each wheel, such as a lock brake system.

Recently, a rotation-sensitive differential limiting mechanism using a viscous coupling has been widely used.
Viscous coupling is a kind of viscous clutch,
Torque is transmitted using the shear resistance of a viscous fluid (such as silicon oil). Therefore, in this type, a smooth differential limiting effect can be obtained in accordance with the rotational difference, but since the initial resistance is given by the viscous fluid, although not as much as the clutch disk crimping type described above, the drive wheels are connected to each other. The result is being restrained.

Accordingly, a differential device having a mechanism for restricting the differential during driving when the driving wheels are not restrained during non-driving and during braking is disclosed in, for example, JP-A-4-271926. In addition, 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.

[0007]

However, in a rotation-sensitive differential limiting mechanism represented by a viscous coupling, the torque transmission rate depends only on the viscosity of the fluid. On the contrary, there is a disadvantage that 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.

The present invention has been made in view of the above problems, and an object of the present invention is to provide a differential device capable of obtaining a reliable differential limiting effect with a simple structure.

[0009]

Means for Solving the Problems The present invention to achieve the above object, housed in claim 1, a pair of rotating bodies which are arranged coaxially opposite each other in the axial direction, each rotary member ,
A predetermined part on the inner side is opposed to each rotating body so that it can contact in the axial direction
Between the case body and the plurality of rolling elements disposed between the axially facing surfaces of the rotating bodies, and between the axially facing surfaces of the rotating bodies.
A holder that is arranged and rotates integrally with the case body ,
A plurality of guide portions extending in the radial direction of the rotating body are provided in the holding body so as to penetrate in the axial direction of the rotating body, and each rolling element is movably accommodated in each guide section, and the axial direction of each rotating body is provided. On the opposing surface, grooves engaging with the rolling elements are provided continuously in the circumferential direction of the rotating body, and when each groove generates a rotation difference, each rolling element reciprocates along the guide portion. Formed into each rotation
When the torque transmitted to the body is constant, the amount of axial reaction force that the groove receives from the rolling element even if the radial distance from the rotating shaft of each rotating body to the rolling element changes Equal
It is formed so as Ku becomes.

According to a second aspect of the present invention, in the differential device according to the first aspect, the groove of each of the rotating bodies includes a first guide for moving the rolling element from one end side to the other end side of the guide portion. A section and a second guide section for moving the rolling element from the other end side of the guide portion toward the one end side continuously in the circumferential direction,
The first guide section of one rotating body is formed longer in the circumferential direction than the second guide section, and the second guide section of the other rotating body is formed longer in the circumferential direction than the first guide section. I have.

[0011]

[0012]

According to a third aspect of the present invention, in the differential device according to the first aspect, the groove of each of the rotating bodies includes a first guide for moving the rolling element from one end side to the other end side of the guide portion. A section, a second guide section for moving the rolling element from the other end side to the one end side of the guide section, and a third guide section for keeping the rolling element at a position within a predetermined range of the guide section in the circumferential direction. One rotating body has a third guiding section in the first guiding section, and the other rotating body has a third guiding section in the second guiding section.
Guide section is provided.

According to a fourth aspect of the present invention, in the differential device according to the first aspect, the groove of each of the rotating bodies includes a first guide for moving the rolling element from one end side to the other end side of the guide portion. A section and a second guide section for moving the rolling element from the other end side of the guide portion toward the one end side continuously in the circumferential direction,
The number of the first or second guide sections of one rotating body and the number of the first or second guide sections of the other rotating body are different from each other.

According to a fifth aspect of the present invention, in the differential device according to the fourth aspect , the groove of each of the rotating bodies is divided into the number of the first or second guide sections of one of the rotating bodies and the number of the first and second guide sections of the other rotating body. The number of the first and second guide sections and the total number of the sections are formed so as to match the number of the rolling elements.

According to a sixth aspect of the present invention, in the differential device according to the fourth or fifth aspect , at least three rotating bodies arranged coaxially with each other are provided, and at least a holding body arranged between the rotating bodies is provided. I have two.

In claim 7 , claims 1, 2, 3,
7. The differential device according to 4, 5, or 6, wherein each of the rotating bodies
Are filled with a viscous fluid that gives resistance to the movement of each rolling element.

According to claim 8 , claims 1, 2, 3,
In the differential device described in 4, 5, 6, or 7, an opening having at least one rotating body having an axial width of at least one rotating body is provided on a side surface of the case body, and each rotating body is provided in the case body. Provide a gap that allows each rotating body to move in the axial direction of the case body so that at least a space equal to or more than the outer diameter of each rolling body is formed between the opposing surfaces, and between the inner surface of the case body and each rotating body is provided. An interposer for holding each rotating body only at the interval of the holding body is provided.

[0019]

According to the differential of the first aspect, when the case body is rotated around the axis, the holding body rotates integrally with the case body.
Then, this rotational force is transmitted to the groove of each rotating body via each rolling body held by the holding body, and each rotating body rotates integrally with the case body. Here, when a rotation difference occurs between the rotating bodies, the rolling bodies accommodated in the guides of the holding body are guided by the grooves of the rotating bodies, roll, and reciprocate along the guides. At that time, the axial reaction force from each rolling element acts on the groove of each rotating body.
So that each rotating body is pressed against the inner surface of the case
The rotational resistance due to frictional force between each rotating body and the case body
And this becomes the differential limiting force. In this case, the magnitude of the reaction force generated between the groove and the rolling element is determined by the shape of the groove. In addition, the grooves of each rotating body have a torque transmitted to each rotating body.
Is constant, the diameter from the rotation axis of each rotating body to the rolling element
Even if the distance in the direction changes, the grooves are formed so that the magnitude of the axial reaction force received from the rolling elements becomes equal, so that the differential limiting force is applied regardless of the rotational position of each rotating body. Is always constant.

According to the differential of the second aspect, in addition to the function of the first aspect, the groove of the one rotating body is formed so that the first guide section is longer in the circumferential direction than the second guide section. Since the second guide section is formed longer in the circumferential direction than the first guide section in the groove of the other rotating body, a position where the rolling element is radially reversed on the opposing surface of each rotating body is provided. They are shifted from each other in the circumferential direction. That is, when the rolling elements reach the reversing positions of the grooves, no force can be transmitted between the rolling elements and the grooves, so by shifting the reversing positions of the respective grooves in the circumferential direction, all the rolling elements At the same time, it does not reach the reversal position.

[0021]

[0022]

According to a third aspect of the present invention, in addition to the function of the first aspect, the third guide section is provided in the first guide section in the groove of one of the rotating bodies, and the other rotating section is provided. Since the third guide section is provided in the second guide section in the groove of the body, the positions at which the rolling elements are radially inverted on the opposing surfaces of the respective rotating bodies are circumferentially similar to each other. It is shifted in the direction. In other words, the rolling element is positioned
When it reaches, the force can be transmitted between the rolling element and the groove.
Can not be shifted, so that the reversal position of each groove is
Because of this, all rolling elements will not reach the reversal position at the same time.
Swell.

According to a fourth aspect of the present invention, in addition to the functions of the first aspect, the number of the first or second guide sections of one of the rotating bodies and the first or second of the other rotating body are provided. And the number of guide sections are different from each other,
The number of positions where the rolling elements are reversed is different in each rotating body, and each rotating body rotates at a different rotating speed. In this case, the rotation ratio of each rotating body is proportional to the reciprocal of the number of the first or second guide section. Further, since the number of reversing positions of the rolling elements is different from each other in the rotating bodies, even if the first or second guide section is symmetrically formed in the circumferential direction, all the rolling elements do not reach the reversing positions at the same time. .

According to the differential of the fifth aspect , in addition to the function of the fourth aspect , in addition to the number of the first or second guide sections of one rotating body and the first or second guiding section of the other rotating body. When the total number of the guide sections is equal to the number of the rolling elements, the state in which the inverted positions of the grooves overlap, that is, the number of the rolling elements that do not transmit the driving force, is minimized.

According to the differential of the sixth aspect, in addition to the function of the fourth or fifth aspect, the number of the first or second guide sections in at least three grooves of the rotating body is arbitrarily set. it means, even when the first or second guide sections circumferentially symmetrical shape, the final rotation ratio of each rotating body 1: it is possible to 1.

According to the differential device of the seventh aspect , in addition to the effects of the first, second, third, fourth, fifth, or sixth aspect, when the rotational speed difference between the rotating bodies increases, each rolling element becomes viscous. or fluid
The differential resistance is limited by this resistance. In this case, due to the nature of the viscous fluid, the differential limiting force is generated so as to gradually increase in accordance with the rotational speed difference between the rotating bodies.

According to the differential device of the eighth aspect , in addition to the effects of the first, second, third, fourth, fifth, sixth or seventh aspect, each rotating body is inserted through the opening of the case body. After moving each rotating body to both axial ends of the case body and inserting each rolling body together with the holding body between the opposing surfaces of each rotating body, each rotating body is moved to the holding body side, and the inner surface of the case body and each Since the assembly is performed by inserting the interposition body between the rotating body and holding each rotating body at the interval of only the holding body, the case body is composed of one part, without using a fastening member such as a bolt. It can be assembled.

[0029]

1 to 10 show a first embodiment of the present invention. FIG. 1 is a side sectional view of a differential gear, FIG. 2 is a sectional view taken along line AA in FIG. FIG. 3 is an exploded perspective view of the differential device.

This differential gear comprises a gear case 1, a gear case cover 2 for closing one end of the gear case 1, and a pair of disk plates 3 arranged coaxially and opposed to each other.
, A center plate 4 disposed between the disc plates 3, and a number of balls 5 rotatably held by the center plate 4. Each disc plate 3 is a rotating body, and the center plate 4 is a Each ball 5 constitutes a rolling element, and each ball 5 constitutes a rolling element.

The gear case 1 has a cylindrical shape with one end opened, and a bearing 1a for supporting one disk plate 3 is provided at the center. A flange 1b is provided around the gear case 1, and the flange 1b is provided with a number of holes 1c for bolt insertion. A groove 1 for fixing the center plate 4 is formed on the inner surface of the gear case 1.
d is provided.

The gear case cover 2 is formed in a disk shape.
A bearing 2a for supporting the other disk plate 3 is provided at the center thereof. A flange 2b is formed around the gear case cover 2, and the flange 2b is provided with a number of holes 2c for bolt insertion. That is, the gear case cover 2 is provided with bolts 2 for fastening the flanges 1b, 2b.
It is assembled to the gear case 1 by d.

The disc plates 3 are formed so that their opposing surfaces are flat, and the other end is provided with a connecting portion 3a for connecting the drive shaft 6 on the wheel side. On the opposing surface of each disk plate 3, there is provided a groove 3b with which each ball 5 is rotatably engaged, and each groove 3b is formed continuously in the circumferential direction. As shown in FIG. 4, each groove 3 b includes a first guide section 3 b-1 for moving the ball 5 from the radial inside to the outside of the disk plate 3, and the ball 5 from the radial outside of the disk plate 3 to the inside. And a second guide section 3b-2 that moves toward the right side in the circumferential direction.
b-1 is formed longer in the circumferential direction than the second guide section 3b-2, and in the other disk plate 3, the second guide section 3b-2 is longer in the circumferential direction than the first guide section 3b-1. Is formed. That is, on the opposing surface of each disk plate 3, the position where the ball 5 is inverted is such that when one of the grooves 3b (outside in FIG. 4) overlaps as shown in FIG. 4, the other (inside in FIG. 4). Are shifted from each other in the circumferential direction. Also, one disk plate 3
A thrust washer 3c is interposed between the disk case 3 and the gear case cover 2 and between the other disk plate 3 and the gear case cover 2, respectively.

The center plate 4 is formed so that both end surfaces are flat, and the groove 4a provided on the peripheral surface thereof and the groove 1 of the gear case 1 are formed.
The gear 4 is fixed in the gear case 1 by a pin 4b fitted to the gear d. The center plate 4 is provided with a total of eight long holes 4c that rotatably accommodate the balls 5 at equal intervals in the circumferential direction. Each long hole 4c extends linearly in the radial direction and penetrates in the axial direction. It is provided. That is, each elongated hole 4c forms a guide.

Each ball 5 is accommodated in each long hole 4c of the center plate 4,
b.

In the differential device constructed as described above, a ring gear (not shown) for transmitting the driving force from the engine is attached to the flange 1b of the gear case 1, and the entire device rotates around the axis of the gear case 1. It is supposed to. That is, when a driving force is input to the gear case 1,
The center plate 4 rotates integrally with the gear case 1, and this rotational force is transmitted to the groove 3 b of each disk plate 3 via each ball 5 and transmitted to the left and right drive shafts 6 connected to each disk plate 3. .

The operation of the differential device is described as follows: when there is no rotation difference between the drive shafts 6; when there is a rotation difference between the drive shafts 6; A case in which the state easily falls will be described.

First, when there is no rotation difference between the drive shafts 6 such as when the vehicle is traveling straight on a road surface having a sufficient frictional force, there is no rotation difference between the disc plates 3. 5 does not occur, and each disk plate 3 rotates integrally with the center plate 4.

Next, when a difference in rotation occurs between the drive shafts 6 in a state where the torque is evenly transmitted to the respective drive wheels, such as when the vehicle is turning on a road surface having a sufficient frictional force, The rotation difference between the drive shafts 6 is allowed by the operation shown in FIG. That is, when each disk plate 3 rotating integrally with each drive shaft 6 causes a rotation difference with respect to each other, the ball 5 in each long hole 4c is guided by each groove 3b and rolls, and the ball 5 in each long hole 4c is rolled. Reciprocating along. That is, the ball 5 was in the inner side in the radial direction in FIG. 4, the first guide section 3b of the grooves 3b, as shown in FIG. 5
Moves toward the outer side in the radial direction along the -1, after reaching the reversal position of the outer side as shown in FIG. 6, each of the second grooves 3b
Moves toward the inner side in the radial direction along the guide section 3b-2 of. In this case, as shown in FIG. 4, every other half of the balls 5 reach the reversal position outside each groove 3b.
On the opposing surface of each disk plate 3, when the inversion position of each groove 3b coincides with one of the inside or outside, the other is shifted from each other, so that the other balls 5 do not reach the inside inversion position. That is, the ball 5 is
When the ball 5 reaches the reverse position, no force can be transmitted between the ball 5 and the groove 3b. Therefore, it is necessary to prevent all the balls 5 from reaching the reverse position of each groove 3b at the same time.

Next, when only one of the drive shafts 6 easily slips, such as when one of the drive wheels loses the frictional force with the road surface, the operation of each drive shaft 6 is performed by the following operation. Differential is limited. That is, each ball
5, the driving force transmitted to each disk plate 3
Since an axial reaction force acts on each groove 3b from each ball 5,
Each disk plate 3 is arranged on the inner side of the gear case 1.
Each thrust washer 3c
Between the disc plate 3 and each thrust washer 3c
Rotational resistance is generated by frictional forces, which
6 is the differential limiting force.

Here, the principle of the differential limiting effect will be described in detail with reference to FIGS. First, FIG. 7 shows the case where the ball 5 and the groove 3b are viewed from the axial direction of the differential device. As shown in FIG.
Is working. Here, A ≒ A '(1) At this time, a force C perpendicular to the contact surface with the ball 5 is generated in the groove 3b, and the component force is A' parallel to the rotational force A, A ' A vertical B. Since C is perpendicular to the contact surface with the ball 5,
Assuming that an angle between A ′ and C (hereinafter, referred to as a contact angle) is located on a line passing through the center of the ball 5 and is α, the size of C is C = A ′ × 1 / cos α ( It is expressed by 2).

Next, as shown in FIG. 8, the ball 5 and the groove 3b
7, the vertical reaction force acting on the contact surface between the groove 3b and the ball 5 is D, and the component force is the axial force of the gear case 1 when viewed from the direction of the arrow Z in FIG. E parallel to the direction and the C perpendicular to E. Hereinafter, E is referred to as a thrust force. Since D is perpendicular to the contact surface with ball 5, it is located on a line passing through the center of ball 5, and the angle between D and C
(Hereinafter referred to as a contact angle) is β, and the magnitude of D is represented by D = C × 1 / cos β (3) Further, the magnitude of the thrust force E is represented by E = C × tan β (4). From the equations (1), (2) and (3), the reaction force D is as follows. D = A × 1 / cos α × 1 / cos β (5) From the equations (1) and (2), C = A × 1 / cos α (6) Also, the thrust force E, which is the other component, is given by equation (1),
From equation (2) and equation (4), E = A × 1 / cos α × tan β (7)

That is, the reaction force D which the ball 5 receives from the groove 3b
Is divided into components C and E, and each thrust washer 3c is pressed in the axial direction by the thrust force E, so that sliding friction is generated around the main shaft and a differential limiting effect is obtained. At this time, by setting the magnitudes of the contact angles α and β between the ball 5 and the groove 3b arbitrarily, it is possible to obtain a necessary differential limiting effect. In addition, thrust washer 3c
By using other inclusions such as bearings instead of, it is also possible to arbitrarily set the degree of the effect of the differential limiting effect by the thrust force E.

When the ball 5 is guided by the groove 3b and moves in each slot 3b, as shown in FIG.
Since the distance between the ball 5 and the spindle S (the axis of the gear case 1) changes, the rotational force A about the spindle S acting on the contact surface between the ball 5 and the groove 3b also changes. Therefore, each disk plate 3
When constant torque transmitted to, for each disc plate 3 is always uniform differential limiting effect even in any rotational position, the contact angle with the variation of the rotational force A alpha
Alternatively, the magnitude of β is continuously changed according to the contact position between the ball 5 and the groove 3b, and the distance from the ball 5 to the main shaft S is changed.
Even if it changes, the thrust force E may be made equal .

First, when the contact angle α is changed, assuming that the distance between the ball 5 and the spindle S at any two positions is L1 and L2 as shown in FIG. 9, the transmission torque T is always constant. Rotational force A1, A acting on ball 5 at position
2 is represented by A1 = T / L1 A2 = T / L2 (8)

Therefore, assuming that the contact angles at the respective positions are α1 and α2, from equations (6) and (8), C = T / L1 × 1 / cosα1 = T / L2 × 1 / cosα2 (9) From the equation (7), the magnitudes of the contact angles α1 and α2 may be set such that E = T / L1 × 1 / cosα1 × tanβ = T / L2 × 1 / cosα2 × tanβ (10) . In this case, β is constant.

Next, when the contact angle β is changed, assuming that the contact angles at the respective positions are β1 and β2, from the equations (6) and (8), C = T / L1 × 1 / cosα = T / L2 × 1 / cosα (11) From the equation (7), from the equation (7), E = T / L1 × 1 / cosα × tanβ1 = T / L2 × 1 / cosα × tanβ2 (12) What is necessary is just to set the magnitude of β2.

As shown in FIG. 10, the position where the same ball 5 comes into contact with each groove 3b comes in contact with the outside in one groove 3b and comes in contact with the inside in the other groove 3b. Therefore,
Even with the same ball 5, since the distances Lo and Li from the contact surface with each groove 3b to the main shaft S are different, the thrust force E generated on each groove 3b side is also different. Therefore, by setting the magnitudes of the contact angles βo, βi with the grooves 3b in accordance with the distances Lo, Li so that the thrust force E becomes constant, (β
o> βi), it is possible to make the differential limiting effect on each disk plate 3 side constant. Note that in FIG.
Illustration of the center plate 4 between the rates 3 is omitted.
However, the force for generating the thrust force E is center play.
This is due to the driving force applied to the ball 5 from the ball 4.

As described above, according to the differential of this embodiment, the ball 5 in each of the long holes 4c is reciprocated along the long hole 4c by the guide of each groove 3b. When a rotational force is applied only from the contact surface, the reaction force which the ball 5 receives from the contact surface with the groove 3b, especially the reaction force in the axial direction
Since the differential is limited by the frictional force of the thrust washer 3c due to the force, it is possible to obtain the effect of reliably limiting the differential of the torque response in operation, and the structure is simple and extremely advantageous for miniaturization. Also, by arbitrarily setting the contact angles α and β between each ball 5 and each groove 3b,
It is also possible to obtain a differential limiting effect as required.

FIGS. 11 to 13 show a second embodiment of the present invention, which differs from the first embodiment in the shape of the groove of the disk plate. That is, in the figure, 7 is a disk plate, 7a is a groove, and 8 is a ball. Groove 7a
Is a first guide section 7a-1 for moving the ball 8 from the radially inner side to the outer side of the disk plate 7, and a second guide section for moving the ball 8 from the radially outer side to the inner side of the disk plate 7. Section 7a-2 and ball 8
Guide section 7a-3 for keeping the position of the disc plate 7 within a predetermined range in the radial direction (in this case, a fixed position in the radial direction).
The first guide section 7a-1 and the second guide section 7a-2 have a distance from the rotation axis of each disk plate 7 to the ball 8 as in the first embodiment. Is formed so that the magnitude of the reaction force received from the ball 8 by the groove 7a is always constant even if the value changes. Further, a third guide section 7a-3 is provided in the first guide section 7a-1 on one disk plate 7, and a third guide section is provided in the second guide section on the other disk plate (not shown). A guidance section is provided. Thus, when the pair of disk plates 7 face each other, as in the first embodiment, when one (inside or outside) inversion position overlaps with each other, the other inversion position is shifted from each other. The groove 7a has a rotation angle of the disc plate 7 of 90 degrees.
゜ is formed so that the ball 8 reciprocates once in the radial direction. When the ball 8 is developed linearly, it becomes as shown in FIG.
The groove 7a is located at the radially inverted position and the third guide section 7a-3.
Does not transmit a force between the ball 8 and the groove 7a, but a second guide section 7a-2 excluding the first guide section 7a-1 transmitting the force and the third guide section 7a-3. In the section, a constant thrust force is always generated as described in the first embodiment. For example, in FIG. 13, a ≦ a ′, b ≧
groove 7a so as to satisfy the conditions of b ', c≤c' and d = d '.
Is formed, any one of the balls 8 can be positioned where the force is transmitted when any ball 8 is in the position where the force is not transmitted, whereby the disk plate 7 can be rotated in any direction. An effective thrust force can always be generated even at a corner.

14 to 19 show a third embodiment of the present invention. FIG. 14 is a side sectional view of a differential device, and FIG.
14 is a sectional view taken along the line AA in FIG. 14, and FIG. 16 is an exploded perspective view of the differential device.

This differential device includes a gear case 10, a gear case cover 11 for closing one end of the gear case 10,
The vehicle includes a pair of disc plates 12 coaxially opposed to each other, a center plate 13 disposed between the disc plates 12, and a number of balls 14 rotatably held by the center plate 13. ing. That is, each disk plate 12 is a rotating body, each center plate 13 is a holding body for holding each rolling element, and each ball 14
Each constitute a rolling element.

The gear case 10 has a cylindrical shape with one end opened, and a bearing 10a for supporting one disk plate 12 is provided at the center. A flange 10b is provided around the gear case 10, and the flange 10b is provided with a number of holes 10c for bolt insertion. A groove 10d for fixing the center plate 13 is provided on the inner surface of the gear case 10.

The gear case cover 11 is formed in a disk shape, and a bearing 11a for supporting the other disk plate 12 is provided at the center thereof. Gear case cover 1
1 is formed around the flange 11b.
b has a number of holes 11c for bolt insertion. That is, the gear case cover 11 includes the flanges 10b,
Gear case 10 by means of a bolt 11d for fastening the gear case 11b.
It is attached to.

The disk plates 12 are formed so that their opposing surfaces are flat, and the other end is provided with a connecting portion 12a for connecting the drive shaft 16 on the wheel side. Each ball 14 is provided on the opposite surface of each disk plate 12.
Are provided so that the grooves 12b are rotatably engaged with each other.
Are formed continuously in the circumferential direction. As shown in FIG. 17, each groove 12 b includes a first guide section 12 b-1 for moving the ball 14 from the radial inside to the outside of the disk plate 12, and the ball 14 from the radial outside of the disk plate 12 to the inside. In the disk plate 12, the first guide section 12b-1 is moved more circumferentially than the second guide section 12b-2. Direction, and the other disk plate 12 has a second guide section 12b-2.
Are formed longer in the circumferential direction than the first guide section 12b-1. That is, on the opposing surface of each disk plate 12, the position where the ball 14 is inverted is such that when one of the grooves 12b (outside in FIG. 17) overlaps as shown in FIG. 17, the other (inside in FIG. 17). Are shifted from each other in the circumferential direction. A thrust washer 12c is interposed between one disk plate 12 and the gear case 10 and between the other disk plate 12 and the gear case cover 11, respectively.

The center plate 13 is formed so that both end faces are flat.
The pin 13b fitted in the groove 10d of the gear case 1
It is fixed within 0. The center plate 13 is provided with a total of ten long holes 13c for rotatably accommodating the respective balls 14 at equal intervals in the circumferential direction. Each long hole 13c extends linearly in the radial direction and penetrates in the axial direction. It is provided. That is, each elongated hole 13c forms a guide. The center plate 13 has a total of four pistons 13d that abut against some of the balls 14, and each piston 13d is slidably accommodated in a total of four holes 13e extending in the radial direction of the center plate 13. . The holes 13 e communicate with each other at the center of the center plate 13, and the inside thereof is filled with a viscous fluid 15. That is, the center plate 13
A communication portion 13f that communicates with each hole 13e is provided at the center of the opening so as to open to the outside.
Is filled in each hole 13e, and the viscous fluid 15 is sealed by a plug 13g fitted into the communication portion 13f. A groove 1 communicating with each hole 13e is formed on the peripheral surface of the plug 13g.
3h are provided, and the inside diameter of the groove 13h is formed smaller than each hole 13e. O-rings 13i and 13j for preventing leakage of the viscous fluid 15 are attached to the peripheral surfaces of the piston 13d and the plug 13g, respectively.

Each ball 14 is accommodated in each slot 13c of the center plate 13, and
2 is engaged with the second groove 12b.

In the differential device configured as described above, when a rotation difference occurs between the respective disk plates 12, FIG.
As shown in FIGS. 7 to 19, each ball 14 rolls while being guided by the groove 12b of each disk plate 12, and reciprocates in the long hole 13c of the center plate 13. At this time, when only one of the disk plates 12 is to be rotated from the drive shaft side, as in the first embodiment, each of the disk plates 12 is connected to each of the thrust washers 12c by the reaction force received by each of the balls 14 from the groove 12b. Thrust force is generated, and the differential force is limited by the frictional force. When each ball 14 reciprocates in the long hole 13c, each piston 13d is pressed by the ball 14 and
3d, and the viscous fluid 15 in each hole 13e flows. That is, since the viscous fluid 15 flows through the groove 13h having a small inner diameter, when the rotational speed difference between the disc plates 12 increases, the resistance of each ball 14 increases due to the flow resistance of the viscous fluid 15, and the difference caused by this resistance. Movement is restricted. In this case, the differential limiting effect is generated so as to gradually increase in accordance with the difference in rotation speed between the disk plates 12.

Therefore, in this embodiment, each ball 14 is
In addition to the torque-sensitive differential limiting effect due to the reaction force received from 2b, a rotational-sensitive differential limiting effect due to the flow resistance of the viscous fluid 15 can also be obtained, so that accurate differential limiting is always performed according to the running state. be able to. The viscous fluid 16 may be a viscous fluid other than silicone oil.

FIGS. 20 to 22 show a fourth embodiment of the present invention. FIGS. 20 and 21 are front views of a disk plate, and FIG. 22 is an exploded perspective view of a main part of a differential device.

In the figure, reference numeral 20 denotes a center plate,
21 is one disk plate, 22 is the other disk plate, and 23 is a ball. The difference from the first embodiment is that the grooves 2 provided in the disk plates 21 and 22 are different.
This is because the shapes of 1a and 22a are different from each other.

The groove 21a of one disk plate 21 shown by a solid line in FIG.
The first guide section 21a-1 that moves from the inner side to the outer side in the radial direction of the
1 has a second guide section 21a-2 that moves inward from the outside in the radial direction to the inside in a circumferential direction, and the guide sections 21a-1 and 21a-2 are the first and second embodiments. has become mutually symmetric shape unlike, it is formed one in the number of disc plates at 21 the first guide section 21a-1 and the second guide section 21a-2 is one by 4 meter. The groove 22a of the other disc plate 22 shown by a broken line in FIG. 20, similar to the one of the disc plate 21, the first guide section 22a-1 and the second guide section 22a-2 of the symmetric shapes Yes However, the number is formed three each. Further, the center plate 20 has a total of seven slots 20.
a is provided, and the number of balls 23 is also seven.

As described above, if the number of guide sections of the grooves 21a and 22a is different, the number of positions for reversing the ball 23 is different from each other. Therefore, each of the disk plates 21 and 22 is rotated at a different rotation speed. The rotation ratio is proportional to the reciprocal of the number of the first or second guide section. That is, in the case of the present embodiment, the rotation ratio between one disk plate 21 and the other disk plate 22 is 4: 3. Therefore, in the differential device of this embodiment, since the rotation ratio of each of the disk plates 21 and 22 is different, the differential device is not a differential device provided between the left and right drive wheels as in the first and second embodiments, but a four-wheel drive. It is used, for example, when torque is transmitted to the front and rear drive shafts of a driving vehicle at different fixed distribution ratios.

In this embodiment, the grooves 21a and 22a are
First guide section 2 on one disk plate 21
1a-1 or the number of the second guide section 21a-2, and the first guide section 22a on the other disk plate 22
By forming so that the total number of -1 or the number of the second guide sections 22a-2 matches the number of the balls 23, the transmission loss of the rotational force can be minimized. That is, since the number of the first or second guide section is four in one disk plate 21 and three in the other disk plate 22, the number of balls 23 is seven. As a result, a state in which the reversal positions of the grooves 21a and 22a overlap each other, that is, a state in which the ball 23 cannot transmit the driving force is only one at a maximum at any rotational angle, and at least a total of six balls 23 are always in each groove 21a. , 22a at an inclined angle with respect to the direction in which the rotational force acts. Also, as shown in FIG. 21, the first guidance section 21b
-1 or the number of the second guide sections 21b-2 is a total of four grooves 21b, and the first guide section 22b-1 or the second guide section 22b-2 is the total of seven grooves 22b. The number of balls 23 and the number of holes 2 in the center plate 20
The number of 0b is 11 each. When the number of the first or second guide section is an even number in each disk plate, the reversal position overlaps at a maximum of two positions.

[0065]

[0066]

[0067]

[0068] Figure 2 3 shows a fifth embodiment of the present invention are those having a total of three center plate, and a total of four of the disc plate. In FIG.
1, 42 are center plates, 43, 44, 45, 46
Is a disk plate, and 47, 48 and 49 are balls.

The first disk plate 43 connected to one of the output shafts faces the second disk plate 44 with the first center plate 40 therebetween.
The opposing surface of the second disk plate 43 is provided with a groove 43 a having a total of six first or second guide sections, and the opposing surface of the second disk plate 44 is provided with a first groove 43 a.
Alternatively, a groove (not shown) in which the number of the second guide sections is formed to be four in total is provided. The first center plate 40 is provided with a total of ten long holes 40a, and each long hole 40a accommodates the same number of balls 47.

The second disk plate 44 is opposed to the third disk plate 45 with the second center plate 41 interposed therebetween.
4 is provided with a groove 44a having a total of five first or second guide sections, and a third disk plate 45 is provided with a groove 44a having the first or second guide section. A total of six grooves (not shown) are provided. Further, the second center plate 41 is provided with a total of eleven long holes 41a, and the same number of balls 48 are accommodated in each long hole 41a.

The third disk plate 45 faces the fourth disk plate 46 connected to the other output shaft with the third center plate 42 interposed therebetween.
The opposing surface of the fourth disk plate 45 is provided with a groove 45a having a total of four first or second guide sections.
Alternatively, a groove (not shown) in which the number of the second guide sections is formed in total of five is provided. The third center plate 42 has a total of nine long holes 42a,
The same number of balls 49 are accommodated in each elongated hole 42a.

[0072] In this configuration, the first disk plate 43 rotates in the forward direction, the second disc plate 44 reverses, the third disc plate 45 forward, and the fourth disc plate 4 6 becomes reversed, both ends Disc plates 43 and 46 rotate in directions opposite to each other. At this time, when the respective rotation ratios are obtained from the number of the first or second guide sections, the rotation ratios are determined in the order from the first disk plate 43 as follows: 1: (− 6/4) :( 5/6): (− 4 / 5) Therefore, when the rotation speed of the first disk plate 43 is 1, the rotation speed of the fourth disk plate 44 is 1 × (−6/4) × (5/6) × (−4/5) = −1, and the rotation ratio of the disk plates 43 and 46 at both ends is 1: 1.

Therefore, if a plurality of center plates and disk plates are combined as in the present embodiment, the number of the first or second guide sections in the groove of each disk plate can be set arbitrarily, whereby Even when the first or second guide section is symmetrical in the circumferential direction, the final rotation ratio of each rotating body can be 1: 1 and the differential device provided between the left and right drive wheels of the automobile Can also be used.

[0074] Figure 2 4 to 2 7 shows a sixth embodiment of the present invention, FIG 2 4 is a side sectional view of a differential device, FIG 5
Is along the line A-A cross-sectional view along a line 2 4, 2 6 along the line B-B cross-sectional view along a line 2 4, 2 7 is an exploded perspective view of the differential gear.

The differential device of this embodiment has a gear case 50
, A gear case cover 51 for closing one end of the gear case 50, a pair of disk plates 52, 53 arranged coaxially opposite each other, and each of the disk plates 52, 53.
A center plate 54 disposed between the center plates 53, and a number of balls 5 rotatably held by the center plate 54.
The space in which each ball 55 moves is filled with a viscous fluid 56 in the gear case 50. That is, each of the disk plates 52 and 53 constitutes a rotating body, the center plate 54 constitutes a holding body, and each ball 55 constitutes a rolling element.

The gear case 50 has a cylindrical shape with one end opened, and a bearing 50a for supporting one disk plate 52 is provided at the center. A flange 50b is provided around the gear case 50, and the flange 50b is provided with a number of holes 50c for bolt insertion. A groove 50d for fixing the center plate 54 is provided on the inner surface of the gear case 50. A total of two filling holes 50e for filling the viscous fluid 56 are provided on the peripheral surface of the gear case 50, and each of the filling holes 50e is closed by the ball 50f after the viscous fluid 56 is filled, and is filled with the filling hole 50e. The ball 50f is fixed by screwing the screw plug 50g. Gear case 5
0 has a plurality of holes 50h for allowing external lubricating oil to flow.
Is provided.

The gear case cover 51 is formed in a disk shape, and a bearing 51a for supporting the other disk plate 53 is provided at the center. Gear case cover 5
1, a flange 51b is formed around the flange 51.
b has a number of holes 51c for bolt insertion. That is, the gear case cover 51 includes the flanges 50b,
It is assembled to the gear case 50 via a sealing O-ring 51e by a bolt 51d that fastens the gear 51b. The gear case cover 51 is provided with a plurality of holes 51f for allowing external lubricating oil to flow.

Each of the disk plates 52 and 53 has a flat surface facing each other, and connection portions 52a and 53a for connecting a drive shaft on the wheel side are provided at the other end. Each of the connecting portions 52a and 53a has a hollow structure penetrating in the axial direction, and one connecting portion 52a is formed longer in the axial direction than the other connecting portion 53a. On the opposing surfaces of the disk plates 52 and 53, grooves 52b and 53b with which the balls 55 are rotatably engaged are provided.
b and 53b are formed continuously in the circumferential direction. That is,
As shown in FIG. 26 , the groove 5 of one disk plate 52
2b is a first guide section 52b for moving the ball 55 from the radially inner side to the outer side of the disc plate 52.
-1 and a second guide section 52b for moving the ball 55 from the radially outer side to the inner side of the disk plate 52.
-2 continuously in the circumferential direction, and the first guide section 52b
-1 is formed longer in the circumferential direction than the second guide section 52b-2. In the other disk plate 53, the second guide section is formed longer in the circumferential direction than the first guide section, and the ball 5 is turned over on the opposing surface of each disk plate 3 as in the first embodiment. The positions to be shifted from each other in the circumferential direction. Further, thrust washers 52c and 53c are interposed between one disk plate 52 and the gear case 50 and between the other disk plate 53 and the gear case cover 51, respectively. Disk caps 52d and 53d for closing the hollow portion are attached to the opposing surfaces of the disk plates 52 and 53, and a seal is provided between the outer peripheral surfaces of the disk caps 52d and 53d and the disk plates 52 and 53. O
Rings 52e and 53e are interposed. Oil seals 52f, 53f are provided between the connecting portions 52a, 53a of the disk plates 52, 53 and the bearings 50a, 51a.
Sealed by.

The center plate 54 has both end faces opposed to the disk plates 52 and 53, and is fixed in the gear case 50 by a groove 54a provided on its peripheral surface and a pin 54b fitted into a groove 50d of the gear case 50. I have.
The center plate 54 is provided with a total of ten long holes 54c for rotatably accommodating the respective balls 5 at equal intervals in the circumferential direction. Each of the long holes 54c extends linearly in the radial direction and extends in the axial direction. Is provided so as to pass through. That is, each long hole 54
c forms a guide. The center plate 54 is provided with a hole 54d penetrating from the outer peripheral surface to the long hole 54c,
The hole 54d communicates with each filling hole 50e of the gear case 50.

Each ball 55 is accommodated in a long hole 54c of the center plate 54, and each of the disc plates 5
2 and 53 are engaged with the grooves 52b and 53b.

The viscous fluid 56 is made of silicon oil or the like, and the grooves 52b, 53b of the disk plates 52, 53 are provided.
And oil seals 52f, 5 in the region including the inside of the long hole 54c of the center plate 54, that is, in the gear case 50.
The space enclosed by 3f is filled.

In the differential device constructed as described above, when a rotation difference occurs between the disk plates 52 and 53, the balls 55 are guided by the grooves 52b and 53b of the disk plates 52 and 53 and roll. Then, it reciprocates in the long hole 54c of the center plate 54. At this time, when only one of the disk plates 52, 53 is to be rotated from the drive shaft side, similarly to the first embodiment, each of the disk plates 52, 53 is subjected to the reaction force received from the groove 52b, 53b. 53 to each thrust washer 52
A thrust force is generated that presses against c and 53c, and the friction force limits the differential. Also, when the difference between the rotational speeds of the disc plates 52 and 53 increases,
Increases from the viscous fluid 56, which also limits the differential. In this case, due to the nature of the viscous fluid 56, the differential limiting effect is generated so as to gradually increase in accordance with the rotational speed difference between the disk plates 52 and 53.

Therefore, in this embodiment, each ball 55 is
In addition to the differential limiting effect of torque response due to the reaction force received from 2b and 53b, similarly to the third embodiment, the differential limiting effect of rotation response due to the resistance of each ball 55 from viscous fluid 56 can be obtained.

[0084] Figure 2 8 through FIG. 3. 1 shows a seventh embodiment of the present invention, FIG. 2 8 is a side sectional view of a differential device, FIG. 29
Is along the line A-A cross-sectional view along a line 2 8, 3 0 along the line B-B cross-sectional view along a line 2 8, 3 1 is an exploded perspective view of an essential part differential.

The differential device of this embodiment has a gear case 60
, A gear case cover 61 for closing one end of the gear case 60, a pair of disk plates 62, 63 arranged coaxially opposite each other,
A center plate 64 arranged between the center plates 63 and a number of balls 6 rotatably held by the center plate 64
The space in which the balls 65 move is filled with a viscous fluid 66 in the gear case 60. That is, each of the disk plates 62 and 63 constitutes a rotating body, the center plate 64 constitutes a holding body, and each ball 65 constitutes a rolling element.

The gear case 60 has a cylindrical shape with one end opened, and a bearing 60a for supporting one disk plate 62 is provided at the center. A flange 60b is provided around the gear case 60, and the flange 60b is provided with a number of holes 60c for bolt insertion. A groove 60d for fixing the center plate 64 is provided on the inner surface of the gear case 60. A total of two filling holes 60e for filling the viscous fluid 66 are provided on the peripheral surface of the gear case 60, and each of the filling holes 60e is
6 is closed with the ball 60f after filling, and the filling hole 6
The ball 60f is fixed by screwing a screw plug 60g into 0e. The gear case 60 is provided with a plurality of holes 60h for allowing lubricating oil from outside to flow.

The gear case cover 61 is formed in a disk shape, and a bearing 61a for supporting the other disk plate 63 is provided at the center thereof. Gear case cover 6
1, a flange 61b is formed around the flange 61.
b has a number of holes 61c for bolt insertion. That is, the gear case cover 61 includes the flanges 60b,
It is assembled to the gear case 60 via a sealing O-ring 61e by a bolt (not shown) that fastens 61b. The gear case cover 61 is provided with a plurality of holes 61f for allowing external lubricating oil to flow.

Each of the disk plates 62 and 63 has a flat surface facing each other, and connection portions 62a and 63a for connecting a drive shaft on the wheel side are provided at the other end. Each of the connecting portions 62a and 63a has a hollow structure penetrating in the axial direction, and one connecting portion 62a is formed longer in the axial direction than the other connecting portion 63a. On the opposing surfaces of the disk plates 62 and 63, grooves 62b and 63b with which the balls 65 rollably engage are provided.
b and 63b are formed continuously in the circumferential direction. That is,
As shown in FIG. 29 , the groove 6 of the other disk plate 63
3b is a first guide section 63b for moving the ball 65 from the radially inner side to the outer side of the disk plate 63.
-1 and a second guide section 63b for moving the ball 65 from the radially outer side to the inner side of the disk plate 63.
-2 continuously in the circumferential direction, and each guide section 63b-
1, 63b-2 have the same contact angle with the ball 65. That is, each guidance section 63b-
As in the fourth embodiment, the first and second guide sections 63b-1 and 63b-2 are symmetrical to each other, and a total of four first guide sections 63b-1 and second guide sections 63b-2 are formed. . Further, similarly to the other disk plate 63, the groove 62b of one disk plate 62 has a first guide section and a second guide section which are symmetrical to each other, and the total number thereof is five. I have. Further, one disk plate 62
Between the gear plate 60 and the other disk plate 63
Thrust washers 62c and 63c are interposed between the gear case cover 61 and the gear case cover 61, respectively. Disk caps 62d and 63d for closing the hollow portion are attached to the opposing surfaces of the disk plates 62 and 63, and a seal is provided between the outer peripheral surfaces of the disk caps 62d and 63d and the disk plates 62 and 63. O-ring 62e, 6
3e is interposed. In addition, each disk plate 6
2, 63 connecting portions 62a, 63a and bearings 60a, 61
is sealed by oil seals 62f and 63f.

The center plate 64 has both end faces opposed to the disk plates 62 and 63, and is fixed in the gear case 60 by a groove 64a provided on its peripheral surface and a pin 64b fitted into a groove 60d of the gear case 60. I have.
The center plate 64 is provided with a total of ten long holes 64c for rotatably accommodating each ball 65 at equal intervals in the circumferential direction, and each long hole 64c extends linearly in the radial direction, and extends in the axial direction. Is provided so as to pass through. That is, each slot 6
4c is a guide part. The center plate 64 is provided with a hole 64d penetrating from the outer peripheral surface to the elongated hole 64c and a hole 64e penetrating from the outer peripheral surface to both end surfaces.
d and 64e communicate with each filling hole 60e of the gear case 60.

Each ball 65 is accommodated in a long hole 64c of the center plate 64, and each of the disc plates 6
2, 63 are engaged with the grooves 62b, 63b. The number of the balls 65 is nine in total based on the theory of the fourth embodiment, based on the number of the guide sections of the disk plates 62 and 63.

The viscous fluid 66 is made of silicon oil or the like, and the grooves 62b, 63b of the disk plates 62, 63 are formed.
And oil seals 62 f, 6 in the region including the inside of the elongated hole 64 c of the center plate 64, that is, in the gear case 60.
The space enclosed by 3f is filled.

In the differential device constructed as described above, similarly to the sixth embodiment, each ball 65 is formed by the grooves 62b, 6b.
A differential limiting effect of torque response due to the reaction force received from 3b and a differential limiting effect of rotation response due to the resistance of each ball 65 from the viscous fluid 66 can be obtained. In the case of the present embodiment, the groove 62b of one disk plate 62 is used.
The total of the number of the first guide section 62b-1 or the second guide section 62b-2 is set to five, and the first guide section 63b-1 or the second guide section in the groove 63b of the other disk plate 63 is set. Since the total number of 63b-2 is set to four, the rotation ratio of each disk plate 62 is 4: 5. Therefore, the differential device according to the present embodiment is used when torque is transmitted to the front and rear drive shafts of a four-wheel drive vehicle at different fixed distribution ratios.

[0093] Figure 3 2 to 3 4 shows an eighth embodiment of the present invention, FIG. 3 2 is a side sectional view of a differential device, FIG 3
Is along the line A-A cross-sectional view along a line 3 2, 3 4 is an exploded perspective view of an essential part differential.

The differential device of this embodiment has a gear case 70
, A gear case cover 71 for closing one end of the gear case 70, a pair of disk plates 72, 73 arranged coaxially opposite to each other, and each disk plate 72, 73.
73, and a number of balls 7 rotatably held by the center plate 74.
The space in which each ball 75 moves is filled with a viscous fluid 76 in the gear case 70. That is, each of the disk plates 72 and 73 constitutes a rotating body, the center plate 74 constitutes a holding body, and each ball 75 constitutes a rolling element.

The gear case 70 has a cylindrical shape with one end opened, and a bearing 70a for supporting one disk plate 72 is provided at the center. A flange 70b is provided around the gear case 70, and the flange 70b is provided with a number of holes 70c for bolt insertion. A groove 70d for fixing the center plate 74 is provided on the inner surface of the gear case 70. A total of two filling holes 70 e for filling the viscous fluid 76 are provided on the peripheral surface of the gear case 70, and each filling hole 70 e is provided with a viscous fluid 7.
6 is filled and closed with a ball 70f,
The ball 70f is fixed by screwing a screw plug 70g to 0e. The gear case 70 is provided with a plurality of holes 70h for allowing lubricating oil from outside to flow.

The gear case cover 71 is formed in a disk shape, and a bearing 71a for supporting the other disk plate 73 is provided at the center. Gear case cover 7
1 is formed around the flange 71b.
b has a number of holes 71c for bolt insertion. That is, the gear case cover 71 includes the flanges 70b,
It is assembled to the gear case 70 via a sealing O-ring 71e by a bolt (not shown) that fastens the gear 71b. The gear case cover 71 is provided with a plurality of holes 71f for allowing external lubricating oil to flow.

The disk plates 72, 73 are formed so that their opposing surfaces are flat, and the other end is provided with connecting portions 72a, 73a for connecting a drive shaft on the wheel side. Each connecting portion 72a, 73a has a hollow structure penetrating in the axial direction, and one connecting portion 72a is formed longer in the axial direction than the other connecting portion 73a. Grooves 72b, 73b are provided on the opposing surfaces of the disk plates 72, 73 so that the balls 75 can roll freely.
b and 73b are formed continuously in the circumferential direction. Each groove 7
The grooves 2b and 73b can be formed in the same manner as the grooves shown in the first embodiment, the second embodiment, or the third embodiment. Omitted. Thrust washers 72c and 73c are interposed between one disk plate 72 and the gear case 70 and between the other disk plate 73 and the gear case cover 71, respectively. Further, disk caps 72d, 73d for closing the hollow portions are attached to the facing surfaces of the disk plates 72, 73, and a seal is provided between the outer peripheral surfaces of the disk caps 72d, 73d and the disk plates 72, 73. O-rings 72e, 7 for
3e is interposed. In addition, each disk plate 7
2, 73 connecting portions 72a, 73a and bearings 70a, 71
is sealed by oil seals 72f and 73f.

The center plate 74 has both end surfaces opposed to the disk plates 72 and 73, and is fixed in the gear case 70 by a groove 74a provided on its peripheral surface and a pin 74b fitted into a groove 70d of the gear case 70. I have.
The center plate 74 is provided with a total of ten long holes 74c for rotatably accommodating the respective balls 75 at equal intervals in the circumferential direction, and each of the long holes 74c extends linearly in the radial direction. Is provided so as to pass through. That is, each slot 7
4c is a guide part.

Each ball 75 is accommodated in a long hole 74c of the center plate 74,
2, 73 are engaged with the grooves 72b, 73b. Each ball 75 is held by a number of plate-shaped ball holders 75a arranged on both sides of the center plate 74, and each ball holder 75a is provided with a hole 75b into which the ball 75 is inserted. That is, each of the long holes 74c of the center plate 74 is covered by each of the ball holders 75a.
4 in the radial direction.

The viscous fluid 76 is made of silicon oil or the like, and the grooves 72b, 73b of the disk plates 72, 73 are provided.
And oil seals 72f and 7 in the region including the inside of the elongated hole 74c of the center plate 74, that is, in the gear case 70.
The space enclosed by 3f is filled.

In the differential device constructed as described above, when a rotation difference occurs between the disk plates 72 and 73, each ball 75 is formed in the groove 7 as in the sixth and seventh embodiments.
The differential is limited by the reaction force received from 2b and 73b. When the difference between the rotational speeds of the disk plates 72 and 73 increases, the resistance of each ball 75 received from the viscous fluid 76 increases, and this resistance limits the differential.
That is, the long hole 7 sealed by each ball holder 75a
When each ball 75 moves in 4c, the viscous fluid 76 flows through a small gap between the inner surface of the elongated hole 74c and the ball 75, and the flow resistance at that time acts as a force for limiting the differential. In this case, the differential limiting effect is
It occurs so as to gradually increase according to the difference between the rotation speeds 2 and 73.

[0102] Figure 3 5 to 3. 7 shows a ninth embodiment of the present invention, FIG. 3 5 is a side sectional view of a differential device, FIG 3 6
Is along the line A-A sectional view taken along line of FIG. 3 5, 3 7 is an exploded perspective view of the differential gear.

The differential device of this embodiment has a gear case 80
A pair of disc plates 81 coaxially opposed to each other, a center plate 82 disposed between the disc plates 81, and a number of balls 83 rotatably held by the center plate 82. It has. That is, each disc plate 81 constitutes a rotating body, the center plate 82 constitutes a holding body, and each ball 83 constitutes a rolling element.

The gear case 80 is formed in a hollow shape, and bearings 80a for supporting the respective disk plates 81 are provided on both end surfaces in the axial direction. A flange 80b is provided around the gear case 80, and the flange 80b is provided with a number of holes 80c for bolt insertion. A center plate 84 is provided on the inner surface of the gear case 80.
A groove 80d for fixing the gear case 80 is provided.
The bearing 80a is interposed on one end surface of the
Is provided. Openings 80f for accommodating other components therein are provided on both side surfaces of the gear case 80.

The disk plates 81 are formed so that their opposing surfaces are flat, and the other end is provided with a connecting portion 81a for connecting a drive shaft on the wheel side. On the opposing surface of each disk plate 81, there is provided a groove 81b with which each ball 83 rollably engages, and each groove 81b is formed continuously in the circumferential direction. Each groove 81b can be formed in the same manner as the groove shown in the first embodiment, the second embodiment or the fourth embodiment, and the operation and effect thereof are the same as those of the above embodiment, so that the description is omitted. I do. A thrust washer 81c is interposed between each disk plate 81 and the inner surface of the gear case 80, and each thrust washer 81c is divided into two parts in the radial direction, and a C-ring fitted to the peripheral surface is provided. They are connected to each other by 81d.

The center plate 82 has both end faces opposed to the respective disc plates 81, and a pin 82 fitted in a groove 82a provided on the peripheral surface thereof and a groove 80d of the gear case 80.
It is fixed in the gear case 80 by b. The center plate 82 is provided with a total of ten long holes 82c that rotatably accommodate the respective balls 83 at equal intervals in the circumferential direction, and each of the long holes 82c extends linearly in the radial direction, and extends in the axial direction. Is provided so as to pass through. That is, each elongated hole 82c forms a guide.

Each ball 83 is accommodated in a long hole 82c of the center plate 82, and each of the disc plates 81
In the groove 81b.

In the differential device configured as described above, when a rotation difference occurs between the disc plates 81, the balls 83 are guided by the grooves 81b of the disc plates 81 and roll, and the balls 83 of the center plate 82 are rotated. It reciprocates in the long hole 82c. At this time, when only one of the disk plates 81 is to be rotated, the thrust force which presses each disk plate 81 against each thrust washer 81c by the reaction force received by each ball 83 from the groove 81b, as in the first embodiment. Is generated, and the differential force is limited by the frictional force.

[0109] In this embodiment, the axial dimension of each portion as shown in FIG. 35 are set as follows. That is, a gap is formed between each disk plate 81 and the end of the bearing 80a so that each disk plate 81 can be moved by D1 at both ends of the gear case 80 without a thrust washer 81c interposed therebetween. The thickness is equal to the thickness of each thrust washer 81c and the center plate 82. Further, as shown by the dashed line in the figure, the distance between the opposing surfaces of the respective disk plates 81 when the respective disk plates 81 are moved to both ends of the gear case 80 is D2.
(= 3D1), which is equal to the outer diameter of the ball 83. Further, the width D3 from the opposing surface of one disk plate 81 moving to the end of the bearing 80a to the edge of the opening 80f on the other disk plate 81 side is at least as long as the other disk plate 81. Have.

The differential device of the present embodiment has the opening 80f of the gear case 80 by setting the dimensions as described above.
The other parts can be accommodated and assembled. Less than,
The procedure will be described.

First, one disk plate 81 is inserted through the opening 80f of the gear case 80, and
In the left bearing 80a in FIG. Next, one disk plate 81 is moved to the end of the bearing 80a, and the other disk plate 81 is moved from between the facing surface of the one disk plate 81 and the end of the opening 80f.
And the other disk plate 81 is inserted into the bearing 80a on the right side in the figure. Then, each disk plate 8
1 is moved to both ends of the gear case 80, and the center plate 82 holding the balls 83 is inserted between the disk plates 81. At this time, the center plate 82 is moved toward any one of the disc plates 81 so that the pins 82b are aligned with the grooves 8 of the center plate 82.
The center plate 82 is fixed to the gear case 80 by fitting into the groove 80d of the gear case 2a. Next, each disk plate 81 is moved to the center side, and the divided thrust washer 81c is inserted between each disk plate 81 and the inner surface of the gear case 80, and each thrust washer 81c is connected by a C ring 81d. . In this case, if each C ring 81d is inserted into each disk plate 81 in advance, each thrust washer 81
c can be easily fitted.

As described above, according to the present embodiment, all the components housed in the gear case 80 can be assembled by inserting them through the openings 80f provided on the side surfaces of the gear case 80. Composed of parts,
It is possible to assemble without using fastening members such as bolts. Therefore, there is an advantage that the number of parts is small, the assembly is easy, and the durability is excellent.

Incidentally, the dimensions D1, D2 shown in the above embodiment are shown.
, D3 are examples. In the above-described embodiment, the width of the opening 80f is formed so that each disk plate 81 is inserted into the gear case 80 one by one.
1 may be formed so as to be inserted at a time with the opposing surfaces facing each other.

[0114] Figure 3 8 to 4 0 shows an example of the first 0 of the present invention, FIG. 3 8 is a side sectional view of a differential device, FIG. 3
9 along the line A-A cross-sectional view along a line 3 8, 4 0 is an exploded perspective view of the differential gear.

The differential device of this embodiment has a gear case 90
A pair of disc plates 91 coaxially opposed to each other, a center plate 92 disposed between the disc plates 91, and a number of balls 93 rotatably held by the center plate 92. It has. That is, each disk plate 91 constitutes a rotating body, the center plate 92 constitutes a holding body, and each ball 93 constitutes a rolling element.

The gear case 90 is formed in a hollow shape, and bearings 90a for supporting the respective disc plates 91 are provided on both end surfaces in the axial direction. A flange 90b is provided around the gear case 90, and the flange 90b is provided with a number of holes 90c for bolt insertion. Center the inner surface of the gear case 90 plates 9 2
A groove 90d for fixing the gear case 90 is provided.
The bearing 90a is interposed on one end surface of the
Is provided. Openings 90f for accommodating other components therein are provided on both side surfaces of the gear case 90, and grooves 9 extending in the radial direction are provided on the right edge of the opening 90f in the drawing.
0 g is provided.

The disc plates 91 are formed so that their opposing surfaces are flat, and the other end is provided with a connecting portion 91a for connecting a drive shaft on the wheel side. On the opposing surface of each disk plate 91, there is provided a groove 91b with which each ball 93 is rotatably engaged, and each groove 91b is formed continuously in the circumferential direction. Each groove 91b can be formed in the same manner as the groove shown in the first embodiment, the second embodiment or the fourth embodiment, and the operation and effect thereof are the same as those of the above embodiment, and therefore the description is omitted. I do. A thrust washer 91c and a lock washer 91d are interposed between each disk plate 91 and the inner surface of the gear case 90, respectively, and each of the washers 91c and 91d is formed to have a partly narrow width in the radial direction. In addition, pawls 91e that lock into the gear case 90 are provided at both ends in the longitudinal direction of each lock washer 91d.
Are formed by bending.

The center plate 92 has both end faces opposed to the respective disc plates 91, and a pin 92 which fits into a groove 92a provided on its peripheral surface and a groove 90d of the gear case 90.
It is fixed in the gear case 90 by b. The center plate 92 is provided with a total of ten long holes 92c which rotatably accommodate the respective balls 93 at equal intervals in the circumferential direction. Each of the long holes 92c extends linearly in the radial direction, and is respectively extended in the axial direction. Is provided so as to pass through. That is, each elongated hole 92c forms a guide.

Each ball 93 is accommodated in a long hole 92c of the center plate 92, and each of the disc plates 91
In the groove 91b.

In the differential device configured as described above, when a rotation difference occurs in each disk plate 91, each ball 93 rolls while being guided by the groove 91b of each disk plate 91, so that the center plate 92 rotates. It reciprocates in the elongated hole 92c. At this time, when only one of the disk plates 91 is to be rotated, the thrust force that presses each disk plate 91 against each thrust washer 91c by the reaction force received by each ball 93 from the groove 91b, as in the first embodiment. Is generated, and the differential force is limited by the frictional force.

In the present embodiment, the dimensions of each part in the axial direction are set in the same manner as in the ninth embodiment. This case is the same as the ninth embodiment except that the superimposed dimension of the thrust washer 91c and the lock washer 91d is equal to the thickness of the thrust washer of the ninth embodiment. I do.

That is, in the differential device of this embodiment, the ninth
Similarly to the embodiment, other parts can be housed and assembled from the opening 90f of the gear case 90. Hereinafter, the procedure will be described.

First, one disk plate 91 is inserted through the opening 90f of the gear case 90 with the thrust washer 91c and the lock washer 91d mounted, and is inserted into the bearing 90a on the left side in the figure of the gear case 90.
At this time, the lock washer 91d on one disk plate 91 does not bend the claw 91e. Next, one disk plate 91 is moved to the end of the bearing 90a, and the other disk plate 91 is moved from between the facing surface of the one disk plate 91 and the end of the opening 90f.
Is inserted with the thrust washer 91c and the lock washer 91d attached, and the other disk plate 91 is inserted into the bearing 90a on the right side in the figure. At this time, the lock washer 91d on the other disk plate 91 side has the claws 91e bent in advance. In addition, each disk plate 9
40, the longitudinal direction thereof is turned by 90 ° with respect to the gear case 90 as shown by the dashed line in FIG.
1d is moved to both ends in the width direction of the opening 90f. Next, each disk plate 91 is moved to both ends of the gear case 90, and a center plate 92 holding each ball 93 is inserted between the disk plates 91.
At this time, the center plate 92 is connected to each disk plate 9
1 so that each pin 92b is inserted into the groove 92a of the center plate 92 and the groove 9a of the gear case 90.
0d and fit the center plate 92 to the gear case 90.
Fixed to. Next, while moving the other disk plate 91 to the center side, each washer 91c, 91d is illustrated.
39 is rotated so that the longitudinal direction thereof coincides with the gear case 90, as shown by the solid line 39 , and the claws 91 of the lock washer 91d are rotated.
e is locked in the gear case 90. Thereafter, one disk plate 91 is moved to the center side, and each washer 91c, 91d is rotated in the same manner as the other disk plate 91 side, and the claw 91e of the lock washer 91d is passed through each hole 90e of the gear case 90 from the outside. It is bent and locked in the gear case 90.

As described above, according to the present embodiment, as in the ninth embodiment, the components accommodated in the gear case 90 can be assembled by inserting all the components through the openings 90f provided on the side surfaces of the gear case 90. it can.

[0125]

As described above, according to the differential of the first aspect, it is not necessary to add a special mechanism for obtaining the differential limiting effect, and the differential limiting effect is stable in response to torque. Can be obtained, so that it can be manufactured extremely small and at low cost. Further, since the differential limiting effect can be arbitrarily set according to the application, there is an advantage that the versatility is excellent. Also transmitted to each rolling element
When the torque is constant, the differential limiting effect can be made equal regardless of the rotational position of each rotating body, so that a stable operation can be obtained.

According to the differential device of the second aspect, in addition to the effect of the first aspect, all the rolling elements do not reach the reversal position of the groove at the same time. The driving force can be transmitted to the motor.

[0127]

Further, according to the differential device of the third aspect , in addition to the effect of the first aspect, similarly to the second aspect, all the rolling elements do not reach the reversal position of the groove at the same time. Driving force can be reliably transmitted to the groove.

According to the differential of the fourth aspect , in addition to the effect of the first aspect, the rotating bodies can be rotated at different rotation ratios from each other, so that the front and rear drive shafts of the four-wheel drive vehicle can be rotated. This is extremely advantageous when torque is transmitted at a different fixed distribution ratio. In this case, even if each groove is symmetrical in the circumferential direction, all the rolling elements do not reach the reverse position at the same time, so that the groove can be easily designed.

According to the differential of the fifth aspect , in addition to the effect of the fourth aspect , the number of rolling elements that do not transmit the driving force can be minimized, so that the transmission loss of the rotational force can be reduced. Can be extremely reduced.

According to the differential device of the sixth aspect , in addition to the effects of the fourth and fifth aspects, the final rotation of each rotating body is achieved even when the groove of each rotating body is formed in a symmetrical shape in the circumferential direction. Since the ratio can be set to 1: 1, it can be used also as a differential device provided between left and right driving wheels of an automobile, and the groove can be easily designed.

According to the differential device of the seventh aspect , in addition to the effects of the first, second, third, fourth, fifth, or sixth aspect, the rotation responsiveness which gradually increases in accordance with the rotational speed difference of each rotating body. Therefore, the differential limiting effect responsive to torque can be effectively applied.

According to the differential device of the eighth aspect , in addition to the effects of the first, second, third, fourth, fifth, sixth or seventh aspect, the case body is formed of one part, and the fastening member such as a bolt is formed. Can be assembled without using any of them, so that there is an advantage that the number of parts is small, the assembly is easy, and the durability is excellent.

[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 an exploded perspective view of the differential device.

FIG. 4 is a diagram illustrating the operation of a differential device.

FIG. 5 is a diagram illustrating the operation of a differential device.

FIG. 6 is an explanatory diagram of the operation of the differential device.

FIG. 7 is an explanatory diagram of an action of a force applied to a groove from a ball.

FIG. 8 is an explanatory diagram of an action of a force applied to a groove from a ball.

FIG. 9 is an explanatory diagram of an action of a force due to a difference in a distance from a main shaft to a ball.

FIG. 10 is an explanatory diagram of an action of a force applied to each disk plate.

FIG. 11 is a front view of a disk plate showing a second embodiment of the present invention.

FIG. 12 is an enlarged view of a groove.

FIG. 13 is an explanatory view in which grooves are developed in a plane.

FIG. 14 is a side sectional view of a differential device according to a third embodiment of the present invention.

FIG. 15 is a sectional view taken along line AA of FIG. 1;

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

FIG. 17 is a diagram illustrating the operation of a differential device.

FIG. 18 is an explanatory diagram of the operation of the differential device.

FIG. 19 is a diagram illustrating the operation of a differential device.

FIG. 20 is a front view of a disk plate according to a fourth embodiment of the present invention.

FIG. 21 is a front view of a disc plate showing another combination of grooves.

FIG. 22 is an exploded perspective view of a main part of the differential device.

FIG. 23 is an exploded perspective view of a main part of a differential gear according to a fifth embodiment of the present invention.

FIG. 24 is a side sectional view of a differential gear according to a sixth embodiment of the present invention.

[Figure 25] A-A direction indicated by the arrow cross-sectional view of FIG. 2 4

[Figure 26] view taken along line B-B cross section view of FIG. 2 4

FIG. 27 is an exploded perspective view of a differential device.

FIG. 28 is a side sectional view of a differential gear according to a seventh embodiment of the present invention.

[29] A-A direction indicated by the arrow cross-sectional view of FIG. 2 8

[Figure 30] view taken along line B-B cross section view of FIG. 2 8

FIG. 31 is an exploded perspective view of a main part of the differential device.

FIG. 32 is a side sectional view of a differential gear according to an eighth embodiment of the present invention.

[33] Figure 3 2 A-A direction indicated by the arrow cross-sectional view

FIG. 34 is an exploded perspective view of a main part of the differential device.

FIG. 35 is a side sectional view of a differential gear according to a ninth embodiment of the present invention.

[Figure 36] A-A direction indicated by the arrow cross-sectional view of FIG. 3 5

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

Side cross-sectional view of a differential gear showing a first 0 embodiment of Figure 38 the present invention

[Figure 39] A-A direction indicated by the arrow cross-sectional view of FIG. 3 8

FIG. 40 is an exploded perspective view of the differential device.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Gear case, 3 ... Disc plate, 3b ... Groove, 3
b-1 first guide section, 3b-2 second guide section,
4 ... Center plate, 4c ... Long hole, 5 ... Ball, 10
... gear case, 12 ... disk plate, 12b ... groove,
12b-1: first guide section, 12b-2: second guide section, 13: center plate, 13c: long hole, 14 ...
Ball, 15: viscous fluid, 20: center plate, 2
0a: long hole, 21, 22: disk plate, 21a,
22a ... groove, 21a-1, 22a-1 ... first guide section, 21a-2, 22a-2 ... second guide section, 23 ...
Ball, 40, 41, 42 ... Center plate, 40
a, 41a, 42a ... long holes, 43, 44, 45, 46 ...
Disc plate, 43a, 44a, 45a ... groove, 4
7, 48, 49: ball, 50: gear case, 52, 5
3. Disc plate, 52b, 53b Groove, 52b-
1, 53b-1 ... first guidance section, 52b-2, 53b
-2: second guide section, 54: center plate, 54
c: long hole, 55: ball, 56: viscous fluid, 60: gear case, 62, 63: disk plate, 62b, 63
b: groove, 62b-1, 63b-1: first guide section, 6
2b-2, 63b-2: second guide section, 64: center plate, 64c: long hole, 65: ball, 66: viscous fluid, 70: gear case, 72, 73: disk plate, 72b, 73b: groove, 72b-1, 73b-1 ... first guide section, 72b-2, 73b-2 ... second guide section, 74 ... center plate, 74c ... long hole, 75 ... ball, 76 ... viscous fluid, 80 ... gear case , 80f ... opening, 81 ... disk plate, 81b ... groove, 83 ... center plate, 83c ... long hole, 84 ... ball, 90 ...
Gear case, 90f: opening, 91: disk plate, 91b: groove, 93: center plate, 93c: long hole, 94: ball.

──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-53-136167 (JP, A) JP-A-58-24649 (JP, A) JP-A-58-77953 (JP, A) JP-A-59-77953 JP 133863 (JP, A) JP-A-60-146954 (JP, A) JP-A-62-2064 (JP, A) JP-A-5-20309 (JP, A) German Patent Invention No. 391583 (DE, C2) U.S. Pat. No. 5,557,423 (US, A) European Patent Application Publication 773390 (EP, A2) (58) Fields investigated (Int. Cl. ⁶ , DB name) 15/40 F16H 25/06 B60K 17/20

Claims (8)

(57) [Claims] 1. A pair of rotating bodies arranged coaxially opposite to each other in the axial direction, each of the rotating bodies being accommodated, and a predetermined portion on the inner surface side being axially aligned with each of the rotating bodies.
A case body which can be brought to face contact with the direction, and a plurality of rolling elements disposed between the facing surfaces of the axial direction of each rotating body is disposed between the facing surfaces of the axial direction of each rotating body, the case body and one
A plurality of guides extending in the radial direction of the rotating body are provided through the holding body in the axial direction of the rotating body, and each rolling element is movably accommodated in each guide. At the same time, grooves that engage with the rolling elements are provided continuously in the circumferential direction of the rotating bodies on the axially opposed surfaces of the rotating bodies. When formed so as to reciprocate along the guide portion and when the torque transmitted to each rotating body is constant, the radial distance from the rotating shaft of each rotating body to the rolling body changes in the groove of each rotating body. A differential device characterized in that the grooves are formed such that the magnitude of the axial reaction force received from the rolling elements is equal . 2. The groove of each of the rotating bodies includes a first guide section for moving a rolling element from one end of the guide portion to the other end, and a groove for moving the rolling element from the other end of the guide portion to one end. And a second guide section to be moved in the circumferential direction,
The first guide section of one rotator is formed longer in the circumferential direction than the second guide section, and the second guide section of the other rotator is formed longer in the circumferential direction than the first guide section. The differential device according to claim 1, wherein: 3. The groove of each of the rotating bodies includes a first guide section for moving a rolling element from one end of the guide to the other end, and a groove for moving the rolling element from the other end of the guide to one end. , And a third guide section that keeps the rolling elements within a predetermined range of the guide section in the circumferential direction, and one of the rotary bodies has the first guide section. A third guide section is provided in the section, and a third guide section is provided in the second guide section for the other rotating body.
2. The differential device according to claim 1, wherein a guide section is provided. 4. The groove of each of the rotating bodies includes a first guide section for moving a rolling element from one end side of the guide section to the other end side, and a rolling section for moving the rolling element from one end side of the guide section to one end side. And a second guide section to be moved in the circumferential direction,
2. The difference according to claim 1, wherein the number of the first or second guide sections of one of the rotating bodies is different from the number of the first or second guide sections of the other rotating body. Motion device. 5. The groove of each of the rotating bodies is a number obtained by summing the number of first or second guiding sections of one rotating body and the number of first or second guiding sections of the other rotating body. 5. The number of rolling elements is equal to the number of rolling elements.
The differential as described. 6. The apparatus according to claim 4, wherein at least three rotating bodies are provided coaxially with each other, and at least two holding bodies are provided between the rotating bodies.
The differential as described. 7. The differential according to claim 1, wherein a viscous fluid that imparts resistance to the movement of each rolling element is filled in the groove of each rotating body. apparatus. 8. A side surface of the case body is provided with an opening through which at least one rotating body having an axial width can be inserted one by one. A gap is provided so that each rotating body can be moved in the axial direction of the case body so that a space larger than the outer diameter is formed, and the space between the inner surface of the case body and each rotating body is only The differential according to claim 1, 2, 3, 4, 5, 6, or 7, further comprising an intermediary body that is held.