JP3247483B2 - Differential torque distribution mechanism - 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 having one input element and two output elements, wherein a torque applied to an input element of the differential device is applied to two output elements at a predetermined ratio. The present invention relates to a torque distribution mechanism of a differential device for distributing.

[0002]

2. Description of the Related Art A differential device provided in a power transmission system of an automobile absorbs a difference in rotational speed between right and left wheels when the automobile turns, and distributes engine torque to the right and left wheels at an appropriate ratio. Is done. However, since a general differential operates according to the difference in load applied to the left and right wheels, when one wheel runs on a road surface with a small friction coefficient and idles, the amount of torque transmitted to the other wheel is reduced. There is a problem that the transmission of torque decreases or the transmission of torque is interrupted.

In order to avoid such inconvenience, a differential device that actively controls a differential device based on the rotation angle and vehicle speed of a steering wheel and distributes a torque suitable for the driving state at that time to left and right wheels. A torque distribution mechanism has already been proposed by the present applicant (JP-A-4-321435).
Reference).

FIG. 3 shows the structure of a torque distribution mechanism of the conventional differential. In the figure, a planetary gear type differential device D to which the driving force of an engine E is transmitted via a transmission M has a ring gear 01 as an input element and a planetary carrier 0 as a first output element.
2, includes a sun gear 03 as a second output element, the planetary carrier 02 is the sun gear 03 is connected to the right wheel W _R is connected to the left wheel W _L. Right wheel W _R and the left wheel W _L planetary gear mechanism P provided in order to distribute the torque includes a sun gear 05 driven by a motor 04, a planetary carrier 06 coupled to the sun gear 03 of the differential device D, the difference And a ring gear 07 connected to the planetary carrier 02 of the moving device D. The connection between the planetary carrier 02 and the ring gear 07 is performed by the external gear 08 provided on the planetary carrier 02.
A pair of spur gears 010 and 011 coaxially engaged with the external gear 09 provided on the ring gear 07 respectively.

[0005] In Thus, by forward and reverse drive the motor 04 at a predetermined rotational speed, the torque of the engine E is transmitted to the right wheel W _R and the left wheel W _L at a predetermined ratio.

[0006]

In order to reduce the size of the torque distribution mechanism of such a differential, it is desirable to use a small and lightweight motor. However, a small and lightweight motor has a small output torque. It is necessary to increase the speed reduction ratio to amplify the torque.

In order to amplify the torque of the motor 04 in the conventional torque distribution mechanism of the differential, the number of teeth of the pinion 012 provided on the output shaft is reduced, and the external gear provided integrally with the sun gear 05 is provided. The number of teeth 013 needs to be set large. However, there is a limit in reducing the number of teeth of the pinion 012, and when the number of teeth of the external gear 013 is increased, there is a problem that the radial size of the torque distribution mechanism increases.

SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned circumstances, and a torque distribution of a differential device capable of using a drive source with a small output torque without increasing the radial size of the torque distribution mechanism. The purpose is to provide a mechanism.

[0009]

In order to achieve the above object, the invention described in claim 1 comprises one input element and two input elements.
A differential device having two output elements, wherein a torque applied to the input element of the differential device is distributed to the two output elements at a predetermined ratio. A first planetary gear mechanism including a first sun gear, a first planetary carrier supporting a first planetary gear meshing with the first ring gear and the first sun gear, a second ring gear, a second sun gear, and the second sun gear. A second planetary gear mechanism comprising a second planetary carrier for supporting a second planetary gear meshing with the ring gear and the second sun gear, wherein the first element of the pair of planetary carriers, the ring gear and the sun gear is connected to the second planetary gear. Two output elements, the second element is non-rotatably connected to each other, and the third element is connected to a different element. Characterized in that coupled to the drive source by a gear ratio.

According to a second aspect of the present invention, in addition to the configuration of the first aspect, the number of teeth of the first ring gear, the first sun gear, and the first planetary carrier constituting the first planetary gear mechanism are each reduced. The second ring gear, the second sun gear, and the second planetary carrier constituting the second planetary gear mechanism are set to have the same number of teeth.

According to a third aspect of the present invention, in addition to the configuration of the first aspect, the differential device includes a ring gear, a sun gear, and a planetary carrier that supports a planetary gear that meshes with the ring gear and the sun gear. It is characterized by becoming.

According to a fourth aspect of the present invention, in addition to the configuration of the first aspect, the driving source is constituted by a hydraulic motor driven by a hydraulic pump connected to the input element. At least one of the hydraulic motors is of a variable displacement type.

According to a fifth aspect of the present invention, in a differential device having one input element and two output elements, a torque applied to an input element of the differential device is predetermined for two output elements. And a first ring gear, a first sun gear,
A first gear meshing with the first ring gear and the first sun gear;
A first planetary gear mechanism including a first planetary carrier supporting the planetary gear, a second ring gear, a second sun gear, and a second planetary carrier supporting the second planetary gear meshing with the second ring gear and the second sun gear; A second planetary gear mechanism, wherein the first planetary carrier and the second planetary carrier are respectively coupled to one and the other of the output elements, and the first sun gear and the second sun gear are connected to each other so as not to rotate relatively, and The first ring gear and the second ring gear are connected to a drive source at different gear ratios.

According to a sixth aspect of the present invention, in a differential device having one input element and two output elements, a torque applied to an input element of the differential device is predetermined for two output elements. And a first ring gear, a first sun gear,
A first gear meshing with the first ring gear and the first sun gear;
A first planetary gear mechanism including a first planetary carrier supporting the planetary gear, a second ring gear, a second sun gear, and a second planetary carrier supporting the second planetary gear meshing with the second ring gear and the second sun gear; A first planetary carrier and a second planetary carrier are respectively connected to one and the other of the output elements, and the first ring gear and the second ring gear are connected to each other such that they cannot rotate relative to each other, and The first sun gear and the second sun gear are connected to a driving source at mutually different gear ratios.

[0015]

Embodiments of the present invention will be described below with reference to the drawings.

FIG. 1 shows a torque distribution mechanism for a differential gear according to a first embodiment of the present invention applied to a front engine / front drive vehicle. As shown in the figure, a transmission M is connected to an engine E mounted horizontally on a vehicle body, and a differential input shaft 1 as an output shaft of the transmission M is driven by a planetary gear type differential D. An input gear 2 for transmitting force is provided.

The differential device D includes a ring gear 4 having an external gear 3 on its outer periphery that meshes with the input gear 2 of the differential device input shaft 1, and a sun gear 5 disposed coaxially inside the ring gear 4. A planetary carrier 8 supporting an outer planetary gear 6 meshing with the ring gear 4 and an inner planetary gear 7 meshing with the sun gear 5 in a state where they mesh with each other. The differential device D, together with the ring gear 4 functions as an input element, the planetary carrier 8 that functions as one output element is coupled to the right wheel W _R through the right shaft 9 functions as the other output element Sun gear 5 is left shaft 10
It is connected to the left wheel W _L through.

Next, the structure of the torque distribution mechanism 11 for distributing the torque input from the ring gear 4 as the input element of the differential device D to the two output elements, the planetary carrier 8 and the sun gear 5, at a predetermined ratio. explain.

The torque distribution mechanism 11 is mounted on the left shaft 10
1st planetary gear mechanism P of the same specification₁And the first
2 planetary gear mechanism P_TwoIs provided. 1st planetary gear mechanism P
₁Is the first planetary carrier 12₁, 1st planetary
Gear 13₁, First sun gear 14₁And the first ring gear
Fifteen₁And the first planetary carrier 1
2 ₁Is a sleeve 16 fitted to the outer periphery of the left shaft 10.
Integrally connected to the planetary carrier 8 of the differential device D via the
Is done.

Meanwhile, the second planetary gear mechanism P _2, the second planetary carrier 12 _2, the second planetary gears 13 ₂ are composed of the second sun gear 14 ₂ and the second ring gear 15 _2, the second planetary carrier 12 ₂ together with coupled to the left shaft 10, the second sun gear 14 ₂ is formed on the first sun gear 14 ₁ integrally.

The torque distribution mechanism 11 includes a hydraulic pump 17 driven by the engine E, and a hydraulic motor 18 driven by oil discharged from the hydraulic pump 17. The hydraulic pump 17 is driven by engaging a pinion 19 fixed to its input shaft with the external gear 3 of the differential device D. Hydraulic motor 18 is adapted to mesh with the external gear 21 the pinion 20 which is fixed to the output shaft is formed in the first ring gear 15 ₁ and the integral of the first planetary gear mechanism P _1, a pinion 22 is fixed to the output shaft meshes with the external gear 23 formed on the second ring gear 15 ₂ and the integral of the second planetary gear mechanism P _2. The reduction ratio from the pinion 20 to the external gear 21 is the pinion 22
The From is set slightly smaller than the reduction ratio of the external gear 23, therefore when driven hydraulic motor 18, the first ring gear 15 of the _first planetary gear mechanism P ₁ is the second planetary gear mechanism P ₂ It is rotated at a slightly greater rotation speed than the second ring gear 15 _2.

Next, the operation of the first embodiment of the present invention having the above configuration will be described.

The hydraulic motor 18 stops while the vehicle is traveling straight.
State, and the pinion 20 and the
Planetary gear mechanism connected through a gear and an external gear 21
P₁First ring gear 15₁And the pinion 22 and outside
Second planetary gear mechanism P connected via tooth gear 23_Twoof
Second ring gear 15_TwoAnd are fixed together. On the other hand,
1, second sun gear 14₁, 14_TwoAre integrally formed
Therefore, the first sun gear 14₁And the first ring gear 15₁When
Planetary gear 13 meshing with₁The first step that supports
Lanetary carrier 12₁Is the second sun gear 14_TwoAnd the second
Ring gear 15_TwoSecond planetary gear 13 meshing with
_TwoSecond planetary carrier 12 that supports _TwoAgainst
It rotates at the same rotation speed in the same direction.

As a result, the first planetary carrier 12 ₁
Shaft 9 integral with the second planetary carrier 12
The left shaft 10 integral with ₂ rotates in the same direction at the same rotational speed, and the rotational speeds of the planetary carrier 8 and the sun gear 5, which are a pair of output elements of the differential device D, are forcibly matched, and the vehicle travels straight. Let it run.

[0025] Now, when the steering wheel to turn the vehicle is operated, the steering angle and the vehicle speed and the required based on a right and left wheels W _R, the rotational speed difference W _L is calculated,
The hydraulic motor 18 is driven in the direction and the number of rotations corresponding to the rotation speed difference. As a result, the first planetary gear mechanism P ₁
The first ring gear 15 ₁ and the second of the second planetary gear mechanism P ₂ of
The ring gear 15 rotates at ₂ and the rotational speed slightly different, first, second ring gear 15 _1, 15 ₂ between differential rotation occurs. Due to this differential rotation, the first and second planetary carriers 1
2 _1, 12 also rotate between ₂ occurs, between the final first planetary carrier 12 ₁ and the right shaft 9 and the second planetary carrier 12 ₂ and the left shaft 10 integral integral, hydraulic motor 18 A differential rotation occurs according to the number of rotations and the direction of rotation. The differential rotation between the right shaft 9 and the left shaft 10 is caused by the outer planetary gear 6 of the differential device D.
And absorbed by the inner planetary gear 7.

The operation of the torque distribution mechanism 11 will be described in more detail.

The rotation speeds of the first and second planetary carriers 12 ₁ and 12 ₂ of the first and second planetary gear mechanisms P ₁ and P ₂ are Nc ₁ and Nc _2, and the first and second ring gears 15 ₁ and 1 are respectively.
5 ₂ the rotational speed and Nr _1, Nr _2, first, the rotational speed of the second sun gear and Ns _1, Ns _2, the rotational speed of the right shaft and N _R, the rotational speed of the left shaft 10 and N _L I do.

As is well known, (1 + λ) Nc ₁ = Nr ₁ + λNs ₁ (1) holds for the first planetary gear mechanism P ₁ , and for the second planetary gear mechanism P ₂ , 1 + λ) Nc ₂ = Nr ₂ + λNs ₂ (2) Here, lambda is the ratio of the sun gear 14 _1, 14 ₂ of the number of teeth Zs for the ring gear 15 _1, 15 ₂ of the tooth number Zr (λ = Zs / Zr) .

When the vehicle is running straight, the hydraulic motor 1
Since 8 is not driven, the ring gear 15 of the _first planetary gear mechanism P ₁ is stopped. Therefore, the expression (1)
By substituting r ₁ = 0, Ns ₁ = ｛(1 + λ) / λ｝ Nc ₁ (3) is obtained, and the ring gear 15 of the second planetary gear mechanism P ₂ is obtained.
_Since Nr ₂ is also stopped, Nr ₂ = 0 is substituted into the above equation (2), and Ns ₂ = ｛(1 + λ) / λ｝ Nc ₂ (4) is obtained.

Since the first and second sun gears 14 ₁ and 14 ₂ are integrally connected, Ns ₁ = Ns _2. Therefore, Nc ₁ = Nc ₂ from the above equations (3) and (4).

That is, the hydraulic motor 18 is not driven
Sometimes, the first planetary carrier 12₁Rotation speed Nc
₁And the second planetary carrier 12_TwoRotation speed Nc_Two
Are kept identical, so that the first planetary carrier 1
2₁Speed N of the right shaft 9 integrated with_RIs the second planetar
Recarrier 12_TwoSpeed N of the left shaft 10 integrated with _L
Becomes the same as

Next, consider the case where the vehicle turns.

When the above equations (1) and (2) are subtracted from each other, (1 + λ) (Nc ₂ −Nc ₁ ) = (Nr ₂ −Nr ₁ ) + λ (Ns ₂ −Ns ₁ ) (5) is obtained. Can be Here, Nc ₂ -Nc ₁ (the differential rotation between the _first and second planetary carriers 12 ₁ and 12 ₂ ) is N _L -N
_R = ΔN (the differential rotation between the right shaft 9 and the left shaft 10) and Ns ₂ −Ns ₁ (the differential rotation between the _first and second sun gears 14 ₁ and 14 ₂ ) are 0. By substituting into the above equation (5), Nr ₂ −Nr ₁ = (1 + λ) ΔN (6) is obtained.

[0034] The formula (6) is between the right shaft 9 and the left shaft 10 to give the differential rotation of .DELTA.N, the hydraulic motor 18 to the first ring gear 15 ₁ and the second ring gear 15 between ₂ (1 + lambda) .DELTA.N of This indicates that a differential rotation should be given.

Assuming that the number of teeth of the pinion 20 is A ₁ , the number of teeth of the pinion 22 is A ₂ , the number of teeth of the external gear 21 is B ₁ , and the number of teeth of the external gear 23 is B ₂ , the hydraulic motor 18 reduction ratio from the first ring gear 15 ₁ i ₁ is i ₁ = B ₁ / a ₁
The second ring gear 15
Reduction ratio i ₂ to ₂ is represented by i ₂ = B ₂ / A _2.

[0036] When the hydraulic motor 18 is driven at a rotational speed Nm, the first ring gear 15 ₁ and the second ring gear 15 ₂
The differential rotation between Nr ₂ -Nr ₁ is given by Nr ₂ −Nr ₁ = Nm / i ₂ −Nm / i ₁ = Nm {(i ₁ −i ₂ ) / i ₁ i ₂ }. (7) Therefore, from the above equations (6) and (7), Nm = ΔN (1 + λ) i ₁ i ₂ / (i ₁ −i ₂ ) = αΔN (8) α = (1 + λ) i ₁ i ₂ / (I ₁ −i ₂ ) (9) is obtained. Here, α is a reduction ratio from the hydraulic motor 18 to the right shaft 9 and the left shaft 10.

The above equation (8) shows that, in order to give a differential rotation of ΔN between the right shaft 9 and the left shaft 10 when the vehicle turns, the rotational speed of the hydraulic motor 18 is reduced by the reduction ratio α = ( 1 + λ) i ₁ i ₂ / (i ₁ −i ₂ ).

In general, the magnitude of the input torque required to exert a predetermined output torque via the power transmission path can be reduced as the reduction ratio of the power transmission path increases. Therefore, Δ between the right shaft 9 and the left shaft 10
The torque of the hydraulic motor 18 required to give N differential rotations can be reduced as the reduction ratio α from the hydraulic motor 18 to the right shaft 9 and the left shaft 10 increases. That is, the torque Tm of the hydraulic motor 18 required to exert the torque T for giving a differential rotation of ΔN between the right shaft 9 and the left shaft 10 is as follows: Tm = T / α = T (i ₁ −i ₂ ) / (1 + λ) i ₁ i ₂ (10)

As is apparent from the equation (10), the torque Tm of the hydraulic motor 18 required to generate a rotational difference ΔN is the reduction ratio i ₁ and the hydraulic motor from the hydraulic motor 18 to the first ring gear 15 ₁ 18 to the second ring gear 15 ₂
By setting the difference i ₁ -i ₂ from the speed reduction ratio i ₂ to a small value, the difference can be arbitrarily reduced. Therefore, it is possible to use a small and lightweight hydraulic motor 18 having a small torque without increasing the number of teeth of the external gears 21 and 23 indiscriminately.

FIG. 2 shows a second embodiment of the present invention.

The relationship between the first embodiment and the second embodiment is as follows.
1, second sun gear 14₁, 14_TwoAnd the first and second phosphorus
Gear 15₁, 15_TwoEquivalent to swapping roles of
You. That is, in the second embodiment, the first and second ring gears 1
5₁, 15_TwoAre formed integrally, and the first sangi
Ya 14₁The external gear 24 formed on the hydraulic motor 18
And meshes with the second sun gear 14_TwoTo
The formed external gear 25 is connected to the pinion 22 of the hydraulic motor 18.
Is engaged. Then, from the pinion 20 to the external gear 2
Reduction ratio to 4 is reduction from pinion 22 to external gear 25
Ratio is set slightly lower than the
When the motor 18 is driven, the first planetary gear mechanism P ₁First Sun
Gear 14₁Is the second planetary gear set P_TwoSecond sun gear 14
_TwoIt is driven to rotate at a slightly higher rotation speed than that.

Thus, according to the second embodiment, the same operation and effect as those of the first embodiment can be obtained.

Although the embodiments of the present invention have been described in detail, the present invention is not limited to the above embodiments, and various design changes can be made.

For example, in the planetary gear type differential device D, which of the ring gear 4, the sun gear 5, and the planetary carrier 8 is used as an input element or an output element can be appropriately changed.

The first and second planetary gear mechanisms P ₁ , P ₂
, A pair of planetary carriers 12
_1, 12 ₂ can be interchanged pair of sun gears 14 _1, 14 ₂ and a pair of ring gears 15 _1, 15 ₂ roles from each other. The first embodiment and the second embodiment show two of the six combinations.

Further, the first planetary gear mechanism P ₁ and the second planetary gear mechanism P ₂ do not necessarily have to have the same specifications in which the number of teeth of each corresponding gear is set to be the same, and the teeth of each corresponding gear are not necessarily required. Similar specifications in which the numbers are set to a fixed ratio may be used.

Further, the torque distribution mechanism of the present invention is applicable not only to the drive system for the front wheels of the vehicle but also to the drive system for the rear wheels.
The present invention is also applicable to torque distribution between front wheels and rear wheels in a four-wheel drive vehicle.

[0048]

As described above, according to the first, fifth, and sixth aspects of the present invention, the driving force is transmitted from the driving source to the first planetary gear mechanism and the second planetary gear mechanism to transmit the driving force to the differential. When performing the differential operation, the torque of the drive source can be reduced without reducing the rotation speed of the drive source at a large reduction ratio. This makes it possible to use a small and lightweight drive source with small torque while setting the number of teeth of the elements connected to the drive source to be small and avoiding an increase in the size of the torque distribution mechanism.

According to the second aspect of the present invention,
Since the number of teeth of each gear constituting the first planetary gear mechanism and the number of teeth of each gear constituting the second planetary gear mechanism are set equal, it is possible to reduce the number of parts and reduce costs.

According to the invention described in claim 3,
The bevel gear is unnecessary because the differential gear is a planetary gear system consisting of a ring gear, a sun gear, a planetary gear and a planetary carrier, and the axial size of the torque distribution mechanism is reduced as compared with the case where a bevel gear differential is adopted. Can be.

According to the fourth aspect of the present invention,
By combining a hydraulic pump and a hydraulic motor, at least one of which is a variable displacement type, the rotation speed of the hydraulic motor can be arbitrarily adjusted with a compact structure.

[Brief description of the drawings]

FIG. 1 is a diagram showing a torque distribution mechanism of a differential gear according to a first embodiment of the present invention.

FIG. 2 is a diagram showing a torque distribution mechanism of a differential gear according to a second embodiment of the present invention.

FIG. 3 is a view showing a torque distribution mechanism of a conventional differential device.

[Explanation of symbols]

Reference Signs List 4 ring gear (input element) 5 sun gear (output element) 6 outer planetary gear (planetary gear) 7 inner planetary gear (planetary gear) 8 planetary carrier (output element) 12 ₁ first planetary carrier 12 ₂ second planetary carrier 13 ₁ first planetary gear 13 ₂ Second planetary gear 14 ₁ First sun gear 14 ₂ Second sun gear 15 ₁ First ring gear 15 ₂ Second ring gear 17 Hydraulic pump 18 Hydraulic motor (drive source) D Differential device P ₁ First planetary gear mechanism P ₂ Second planetary gear mechanism

────────────────────────────────────────────────── ─── Continuation of the front page (56) References JP-A-3-525 (JP, A) JP-A-4-321435 (JP, A) US Patent 5,358,583 (US, A) US Patent 5,518,463 (US, A) German Patent Invention 4408587 (DE, C2) (58) Field searched (Int. Cl. ⁷ , DB name) F16H 48/30 B60K 23/04

Claims (6)

(57) [Claims] 1. A differential (D) having one input element (4) and two output elements (5, 8) added to the input element (4) of the differential (D). Torque 2
A torque distribution mechanism for a differential device for distributing a predetermined ratio to two output elements (5, 8), comprising: a first ring gear (15 ₁ ) and a first sun gear (14 ₁ )
And a first planetary gear mechanism (P ₁ ) comprising a first planetary carrier (12 ₁ ) supporting a first planetary gear (13 ₁ ) meshing with the first ring gear (15 ₁ ) and the first sun gear (14 ₁ ). ) And the second ring gear (1
5 ₂ ), a second sun gear (14 ₂ ), and a second planetary carrier (12 ₂ ) supporting the second ring gear (15 ₂ ) and the second planetary gear (13 ₂ ) meshing with the second sun gear (14 ₂ ). ) and a more becomes the second planetary gear mechanism (P _2), each pair of planetary carrier (12 _1, 12 _2), a ring gear (15 _1, 15 ₂₎ and the sun gear (14 _1, 14 ₂₎ of the Are connected to the two output elements (5, 8) respectively, the second elements are connected to each other so as not to rotate relative to each other, and the third element is connected to the drive source with a different gear ratio. (18) A torque distribution mechanism for a differential gear, which is connected to (18). Wherein said first first ring gear which constitutes a planetary gear mechanism (P ₁₎ (15 _1), the first sun gear (14 ₁₎
The number of teeth of the first planetary carrier (12 ₁ ) and the number of teeth of the second planetary gear mechanism (P ₂ ) are set to the second ring gear (15 ₂ ), the second sun gear (14 ₂ ), and the second planetary carrier (12 1). _2. The torque distribution mechanism for a differential according to claim 1, wherein the number of teeth is set to be equal to the number of teeth of ₂ ). 3. The differential gear (D) includes a ring gear (4), a sun gear (5), and a planetary gear (6) meshing with the ring gear (4) and the sun gear (5).
The torque distribution mechanism for a differential according to claim 1, further comprising a planetary carrier (8) for supporting (7). 4. The hydraulic pump (1), wherein the drive source (18) comprises a hydraulic motor (18) driven by a hydraulic pump (17) connected to the input element (4).
The torque distribution mechanism according to claim 1, wherein at least one of the hydraulic motor (7) and the hydraulic motor (18) is of a variable displacement type. 5. In a differential (D) comprising one input element (4) and two output elements (5, 8), it is applied to the input element (4) of the differential (D). Torque 2
A torque distribution mechanism for a differential device for distributing a predetermined ratio to two output elements (5, 8), comprising: a first ring gear (15 ₁ ) and a first sun gear (14 ₁ )
And a first planetary gear mechanism (P ₁ ) comprising a first planetary carrier (12 ₁ ) supporting a first planetary gear (13 ₁ ) meshing with the first ring gear (15 ₁ ) and the first sun gear (14 ₁ ). ) And the second ring gear (1
5 ₂ ), a second sun gear (14 ₂ ), and a second planetary carrier (12 ₂ ) supporting the second ring gear (15 ₂ ) and the second planetary gear (13 ₂ ) meshing with the second sun gear (14 ₂ ). ) and become more second planetary gear mechanism (P ₂₎ and comprising a first planetary carrier (12 ₁₎
And the second planetary carrier (12 ₂ ) are coupled to one and the other of the output elements (5, 8), respectively, and the first sun gear (14 ₁ ) and the second sun gear (14)
₂ ) and the first ring gear (1)
5 ₁₎ and the second ring gear (15 _2), characterized in that coupled to the drive source (18) at mutually different gear ratio, the torque distribution mechanism of the differential device. 6. A differential (D) having one input element (4) and two output elements (5, 8), which is applied to the input element (4) of the differential (D). Torque 2
A torque distribution mechanism for a differential device for distributing a predetermined ratio to two output elements (5, 8), comprising: a first ring gear (15 ₁ ) and a first sun gear (14 ₁ )
And a first planetary gear mechanism (P ₁ ) comprising a first planetary carrier (12 ₁ ) supporting a first planetary gear (13 ₁ ) meshing with the first ring gear (15 ₁ ) and the first sun gear (14 ₁ ). ) And the second ring gear (1
5 ₂ ), a second sun gear (14 ₂ ), and a second planetary carrier (12 ₂ ) supporting the second ring gear (15 ₂ ) and the second planetary gear (13 ₂ ) meshing with the second sun gear (14 ₂ ). ) and become more second planetary gear mechanism (P ₂₎ and comprising a first planetary carrier (12 ₁₎
And the second planetary carrier (12 ₂ ) are connected to one and the other of the output elements (5, 8), respectively, and the first ring gear (15 ₁ ) and the second ring gear (15 ₂ ) are connected to each other so that they cannot rotate relative to each other. And a first sun gear (14 ₁ ) and a second sun gear (14 ₂ ) connected to a drive source (18) with different gear ratios from each other.