Differential gear

Abstract: The present invention aims at realizing with a simple structure a differential gear capable of arbitrarily producing a difference in speed of rotation between output side rotary members. When a difference in speed of rotation occurs between drive shafts 3 and 4, if clutches 12 and 17 are disconnected, a first input side sun gear 8 and a first output side sun gear 9 are allowed to rotate at arbitrary speed ratios independently of each other due to the rotation and the revolution of first planetary gears 10, besides a second input side sun gear 13 and a second output side sun gear 14 are allowed to rotate at arbitrary speed ratios independently of each other due to the rotation and the revolution of second planetary gears 15. When the first clutch 12 for example is brought into connection, the revolution of the first planetary gears 10 is controlled. Thus, by setting appropriately the gear ratio between the sun gears 8, 9 and gears 10a, 10b of the first planetary gear 10, the drive shaft 3 on one hand is allowed to rotate faster than the drive shaft 4 on the other.

Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a differential gear according to the preamble of single claim 1. 2. Description of the Related Art. A differential gear of the above kind is disclosed, for example, by document FR 670 026 A, which represents the closest state of the art. This differential gear comprises an input side rotary member for receiving an external driving force, a pair of output side rotary members arranged coaxially with the rotational axis of the input side rotary member, and a gear body for free-rotatably supporting the input side rotary member and the output side rotary members. The differential gear further comprises a first input side gear disposed on one end side of the input side rotary member, a second input side gear which rotates jointly with said input side rotary member, a first output side gear having a deceleration ratio larger or smaller relative to said first input side gear and rotating jointly with one of said output side rotary members. A second output side gear has a deceleration ratio larger or smaller relative to said second input side gear. At least one first planetary gear meshes with said first input side gear and said first output side gear, and at least one second planetary gear meshes with said second input side gear and said second output side gear. A similar arrangement is known from DE 18 10 961, which shows a differential gear with at least one driving shaft rotating a gear body, while wheels are rotatably supporting inside the gear body, said wheels being jointly connected to the driving shafts. Moreover, EP-A-0 546 733 shows a drive power distributation control system for vehicles, which is suitable for use in distributing drive power to different drive wheels or to transfer the drive power between a left and right non-drive wheels. The proposed arrangement comprises a differential mechanism for transmittling the drive power to the shafts and a drive power transmission control mechanism for controlling the distribution of the drive power. The mechanism is constructed of a speed change mechanism capable of changing and outputting rotational speeds of the shafts and a drive power transmission mechanism capable of transmitting drive force between a casing and a second sun gear of the speed change mechanism. A differential gear for the motor vehicle is a unit for permitting a difference in speed of rotation between right and left driving wheels which may occur when the motor vehicle is moving in a curve, or a difference in speed of rotation between front and rear driving wheels of a motor vehicle with four-wheel drive. A typical arrangement of the differential gear is such that a pinion gear intervenes between a pair of bevel gears coupled to output shafts, and that when an external rotational force is applied to the pinion gear shaft, the pinion gear rotates on its own axis at the time of occurrence of a differential motion so as to permit a difference in speed of rotation between the output shafts. By the way, when the motor vehicle turns along a curve, a difference in speed of rotation occurs between the inner wheel and the outer wheel is permitted by the above-described differential gear, the difference in speed of rotation being caused attendantly as a result of a frictional force between the wheels and the surface of a road. It is thus possible to enhance the turning performance or the high-speed stability by positively generating the difference in speed of rotation between the driving wheels. If, for instance, the left-hand wheel is rotated faster than the ordinary rotational speed upon a rightward turning, then the handling operation for turning will be facilitated. Also, when the motor vehicle is subjected to a strong lateral wind upon a straight movement, if the wheel on the downwind side is rotated faster than the wheel on the opposite side, the automobile can be prevented from being transversely urged without any extreme handling operation. Accordingly, the realization of such a unit with a simple structure would be very effective in enhancing the performance of the motor vehicles. SUMMARY OF THE INVENTION The present invention was conceived in view of the above problems. It is therefore an object of the present invention to realize with a simple structure a differential gear capable of arbitrarily generating a difference in speed of rotation between output side rotary members. In order to achieve the above object, there is provided a differential gear according to the single main claim. Thus, when a difference in speed of rotation takes place between the output side rotary members, if the rotation controlling means are released, then the first input side gear rotating jointly with the input side rotary member and the first output side gear rotating jointly with one of the output side rotary members are allowed to rotate at arbitrary speed ratios independently of each other due to the rotation and the revolution of the first planetary gears, besides the second input side gear rotating jointly with the input side rotary member and the second output side gear rotating coaxially with one of the output side rotary members are allowed to rotate at arbitrary speed ratios independently of each other due to the rotation and the revolution of the second planetary gears. When the rotation of the first support member is controlled by the first rotation controlling means, the rotation of the first planetary gear is controlled, with the result that by setting appropriately the gear ratios between the first input side gear, the first output side gear and the first planetary gears, one of the output side rotary members for instance can be controlled to rotate faster than the other output side rotary member. On the contrary, when the rotation of the second support member is controlled by the second rotation controlling means, the rotation of the second output side gear is controlled, with the result that by setting appropriately the gear ratios between the second input side gear, the second output side gear and the second planetary gears, the other output side rotary member for instance can be controlled to rotate faster than the one of the output side rotary members. Thus, according to the present invention, there can be realized with the simple structure the differential gear capable of arbitrarily generating a difference in speed of rotation between the output side rotary members, whereby the turning performance can be enhanced by rotating the outside driving wheel faster than the inside driving wheel in a curve when a motor vehicle turns for instance, which will remarkably contribute to an improvement in performance of the motor vehicle. BRIEF DESCRIPTION OF THE DRAWINGS The above and other objects, aspects, features and advantages of the present invention will become more apparent from the following detailed description with reference to the accompanying drawings, in which: Fig. 1 is sectional side elevation of an embodiment of a differential gear in accordance with the present invention; and Fig. 2 is a schematic view of the differential gear shown in Fig. 1. DESCRIPTION OF THE PREFERRED EMBODIMENTS Fig. 1 illustrates an embodiment of a differential gear in accordance with the present invention, the differential gear being interposed between right and left driving wheels of a motor vehicle. The differential gear of this embodiment comprises a gear body 20 fixedly secured to the vehicle body, a gear case 21 receiving a driving force from the vehicle engine, and a pair of drive shafts 22 and 23 arranged coaxially with the rotational axis of the gear case 21. A rotational force of the gear case 21 is transmitted to the drive shafts 22 and 23 while permitting a difference in speed of rotation of the drive shafts 22 and 23. In this case, the drive shaft 22 on one hand is coupled to the right-hand driving wheel of the motor vehicle, and the drive shaft 23 on the other is coupled to the left-hand driving wheel of the motor vehicle. More specifically, the gear case 21 includes a ring gear 21a which is engaged with a propeller shaft 24 rotated by a driving force from the engine. The drive shafts 22 and 23 include at their one ends respective bevel gears 25 which are meshed with each other by way of a plurality of pinion gears 26. In this case, the pinion gears 26 are supported by a pinion shafts 26a fixedly secured to the gear case 21 and rotate jointly with the gear case 21. On one end side of the gear case 21, there are provided a first input side sun gear 27 rotating jointly with the gear case 21, a second input side sun gear 28 also rotating jointly with the gear case 21, a first output side sun gear 29 rotating jointly with the drive shaft 22 on one hand, a second output side sun gear 30 rotating coaxially with the drive shaft 22 on one hand, a plurality of first planetary gears 31 meshing with the first input side sun gear 27 and the first output side sun gear 29, a plurality of second planetary gears 32 meshing with the second input side sun gear 28 and the second output side sun gear 30, a carrier 33 for rotatably supporting the first and second planetary gears 31 and 32 on their own axes, a first clutch 34 for controlling the rotation of the carrier 33 with an arbitrary controlling force, and a second clutch 35 for controlling the rotation of the second output sun gear 30 with an arbitrary controlling force. The first input side sun gear 27 and the first output side sun gear 29 are so formed as to be different in size from each other, and each of the first planetary gears 31 axially integrally includes gears 31a and 31b meshing with the sun gears 27 and 29. The second input side sun gear 28 and the second output side sun gear 30 are so formed as to be different in size from each other and each of the second planetary gears 32 axially integrally includes gears 32a and 32b meshing with the sun gears 28 and 30. The carrier 33 is provided rotatably around the rotational axis of the drive shaft 22 on one hand, and supports the first planetary gears 31 rotatably around the rotational axis of the drive shaft 22 on one hand. The first clutch 34 is interposed between the carrier 33 and the gear body 20, and includes a plurality of friction plates 34a supported on the carrier 33 side and a plurality of friction plates 34b supported on the gear body 20 side. The friction plates 34a and 34b are alternately arranged and pressure bonded to each other with an arbitrary pressing force by a hydraulic cylinder 34c, to thereby control the rotation of the carrier 33. In this instance, the hydraulic cylinder 34c is connected via an oil communication port 34d to a hydraulic driving circuit not shown. On the contrary, the second clutch 35 is interposed between the second output side sun gear 30 and the gear body 20, and includes a plurality of friction plates 35a supported on the output side sun gear 30 side and a plurality of friction plates 35b supported on the gear body 20 side. The friction plates 35a and 35b are alternately arranged and pressure bonded to each other with an arbitrary pressing force by a hydraulic cylinder 35c, to thereby control the rotation of the output side sun gear 30. In this instance, the hydraulic cylinder 35c is connected via an oil communication port 35d to a hydraulic driving circuit not shown, in the same manner as the first clutch 34. In the above configuration, when the gear case 21 receives a driving force from the engine by way of the propeller shaft 24, the gear case 21 rotates coaxially with the drive shafts 22 and 23 in the same manner as the first embodiment, and a rotational force of the gear case 21 is transmitted to the drive shafts 22 and 23 by way of the pinion gears 26 and the bevel gears 25. At that time, if a difference in speed of rotation occurs between the drive shafts 22 and 23 for example when the motor vehicle runs along a curve, then the pinion gears 26 rotates on their own axes to permit the difference in speed of rotation between the drive shafts 22 and 23. In this instance, if the clutches 34 and 35 are disconnected, the first input side sun gear 27 rotating jointly with the gear case 21 and the first output side sun gear 29 rotating jointly with the drive shaft 22 on one hand are allowed to rotate at arbitrary speed ratios independently of each other due to the rotation and the revolution of the first planetary gears 31, besides the second input side sun gear 28 rotating jointly with the gear case 21 and the second output side sun gear 30 rotating coaxially with the drive shaft 23 are allowed to rotate at arbitrary speed ratios independently of each other due to the rotation and the revolution of the second planetary gears 32. When the first clutch 34 is brought into a connection herein, the rotation of the carrier 33, that is, the revolution of the first planetary gears 31 is controlled, with the result that when the carrier 33 for instance is entirely fixed, the drive shafts 22 and 23 are so controlled as to rotate at arbitrary speed ratios independently of each other on the basis of the gear ratios between the first input side sun gear 27, the first output side sun gear 29 and the gears 31a, 31b of the first planetary gear 31. Let the number of teeth of the first input side sun gear 27 be Za, the number of teeth of the gears 31a and 31b be Zb and Zc, respectively, and the number of teeth of the first output side sun gear 29 be Zd. Then, per rotation of the gear case 21, the first planetary gears 31 are allowed to rotate on their own axes by -Za/ Zb Therefore, the right-hand drive shaft 22 rotates by (Za/ Zb) (Zc/ Zd) and the left-hand drive shaft 23 rotates by 2 - (Za/ Zb) (Zc/ Zd) Hence the speed ratio between the right-hand drive shaft 22 and the left-hand drive shaft 23 results in (Za/ Zb) (Zc/ Zd) : 2 - (Za/ Zb) (Zc/ Zd) In this instance, Za> Zd, and Zb< Zc. Hence, by setting Za, Zb, Zc and Zd so as to become (Za/ Zb) (Zc/ Zd) > 1 the left-hand drive shaft 23 is allowed to rotate faster than the right-hand drive shaft 22. Also, the disconnection of the first clutch 34 and the connection of the second clutch 35 will result in a control of the rotation of the second output side sun gear 30, so that when the second output side sun gear 30 for instance is entirely fixed, the carrier 33 and the gear case 21 are so controlled as to rotate at mutually arbitrary speed ratios on the basis of the gear ratios between the second input side sun gear 28, the second output side sun gear 30 and the gears 32a and 32b of the second planetary gear 32. Let the number of teeth of the second output side sun gear 30 be Ze, the number of teeth of the gears 32a and 32b be Zf and Zg, respectively, and the number of teeth of the second input side sun gear 28 be Zh. Then, per rotation of the carrier 33, the second planetary gear 32 rotates on its own axis by Ze/ Zf That is, the rotation of the second planetary gear 32 on its own axis given as - (Ze/ Zf) (Zg/ Zh) is added to one revolution of the second planetary gear 32, with the result that for each rotation of the carrier 33 the gear case 21 is allowed to rotate by 1 - (Ze/ Zf) (Zg/ Zh) Furthermore, the first input side sun gear 27 rotates jointly with the gear case 21 and then the second planetary gear 31 also rotates, so that the rotation of the first planetary gear 32 on its own axis expressed as - [ 1 - {1 - (Ze/ Zf) (Zg/ Zh)} ] x (Za/ Zb) (Zc/ Zd) is added to one revolution of the first planetary gear 31, allowing the right-hand drive shaft 22 to rotate by 1 - [1 - {1 - (Ze/ Zf) (Zg/ Zh)}] x (Za/ Zb) (Zc/Zd) Accordingly, the speed ratio between the gear case 21 and the right-hand drive shaft 22 results in 1 - (Ze/ Zf) (Zg/ Zh) : 1 - [1 - {1 - (Ze/ Zf) (Zg/ Zh)}] x (Za/ Zb) (Zc/ Zd) Thus, by setting Ze, Zf, Zg and Zh so that the speed ratio between the right-hand drive shaft 22 and the left-hand drive shaft 23 becomes reverse to the case of connection of the first clutch 34, that is, becomes 2 - (Za/ Zb) (Za/ Zb): (Za/ Zb) (Za/ Zb) the right-hand drive shaft 22 is allowed to rotate faster than the left-hand drive shaft 23.

Claims: A differential gear having an input side rotary member (21) for receiving an external driving force, a pair of output side rotary members (22,23) arranged coaxially with the rotational axis of the input side rotary member (21), and a gear body (20) for free-rotatably supporting the input side rotary member (21) and the output side rotary members (22,23), with a rotational force of the input side rotary member (21) being transmitted to the output side rotary members (22,23) while permitting a difference in speed of rotation between the output side rotary members (22,23), said differential gear comprising: a first input side gear (27) disposed on said input side rotary member (21) at its one end side in the axial direction, said first input side gear (27) rotating jointly with said input side rotary member (21); a second input side gear (28) disposed on said input side rotary member (21), said second input side gear (28) rotating jointly with said input side rotary member (21); a first output side gear (29) having a deceleration ratio larger or smaller relative to said first input side gear (27), said first output side gear (29) rotating jointly with one of said output side rotary members (22,23); a second output side gear (30) having a deceleration ratio larger or smaller relative to said second input side gear (28), at least one first planetary gear (31) meshing with said first input side gear (27) and said first output side gear (29); at least one second planetary gear (32) meshing with said second input side gear (28) and said second output side gear (30); being characterized in that said second input side gear (28) is disposed on said input side rotary member (21) at its one end side in the axial direction; said second output side gear (30) is rotating coaxially with said one of said output side rotary members (22,23); and that said differential gear further comprises a support member (33) for supporting said first planetary gear (31) and said second planetary gear (32) to be able to rotate coaxially on their own axes and to revolve around the rotational axis of said input side rotary member (21); a first rotation controlling means (34) for controlling with an arbitrary controlling force the rotation of the said support member (33) around the rotational axis of said input side rotary member (21); and a second rotation controlling means (35) for controlling with an arbitrary controlling force the rotation of the said second output side gear (30), wherein said rotation controlling means (34,35) include a plurality of friction plates (34a,35a) rotating jointly with said support member (33) or said second output side gear (30), a plurality of friction plates (34b,35b) rotating jointly with said gear body (20), and pressing means (34c,35c) for pressure bonding the friction plates (34a,35a; 34b,35b) to each other with an arbitrary pressing force.

Inventors: MIMURA KENJI, MIMURA, KENJI
Applicants: MIMURA KENJI, MIMURA, KENJI
Application year: 1997
Main classification: F16H48
IPC codes: F16H48, F16H37, B60K17, B60K23