CN106838202B - Limited slip differential - Google Patents
Limited slip differential Download PDFInfo
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- CN106838202B CN106838202B CN201710215142.3A CN201710215142A CN106838202B CN 106838202 B CN106838202 B CN 106838202B CN 201710215142 A CN201710215142 A CN 201710215142A CN 106838202 B CN106838202 B CN 106838202B
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- 230000007246 mechanism Effects 0.000 claims description 20
- 230000003068 static effect Effects 0.000 claims description 2
- 230000033001 locomotion Effects 0.000 description 8
- 230000005540 biological transmission Effects 0.000 description 6
- 230000009286 beneficial effect Effects 0.000 description 4
- 238000006073 displacement reaction Methods 0.000 description 3
- 230000009347 mechanical transmission Effects 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 238000005461 lubrication Methods 0.000 description 2
- 239000003921 oil Substances 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000009699 differential effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
- F16H48/22—Arrangements for suppressing or influencing the differential action, e.g. locking devices using friction clutches or brakes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/12—Differential gearings without gears having orbital motion
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
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Abstract
The invention relates to a limited slip differential, in particular to a limited slip differential which can be used for an automobile, and comprises a shell, an internal gear pair formed by a swing gear A and an output gear A, an internal gear pair formed by a swing gear B and an output gear B, at least two A-type intermediate gears, at least two B-type intermediate gears and at least two friction plates; the radial direction of each A-type intermediate gear is fixed with the shell, the rotation axis is parallel to the rotation axis of the shell, each A-type intermediate gear is meshed with at least one B-type intermediate gear, the gear pair gear ratio of each A-type intermediate gear and each B-type intermediate gear is the same, the eccentric shafts with the axes parallel to the rotation axis are arranged on each A-type intermediate gear, the distances between the eccentric shafts on each A-type intermediate gear and the rotation axes of the gears are the same, the phases of the eccentric shafts on all A-type intermediate gears are the same, the eccentric shafts on each A-type intermediate gear are radially fixed with the swing gear A respectively, and the output gear A is coaxial with the rotation axes of the shell.
Description
Technical Field
The invention relates to a limited slip differential, in particular to a limited slip differential applicable to automobiles, and belongs to the technical field of mechanical transmission parts.
Background
The differential is a mechanical transmission part, is used for transmitting power output by an automobile gearbox to two or four driving wheels, and is mostly in a bevel gear or crown gear structure because the tracks pressed by the driving wheels are different due to uneven road surfaces, cornering and the like, and friction between the driving wheels and the road surfaces is increased and the running resistance of the vehicle is increased if the driving wheels rotate at the same speed, so that the differential needs to output rotating speed to the wheels according to different running conditions of each driving wheel.
Limited slip differential, english name LIMITED SLIP DIFFERENTIAL, LSD for short. The limited slip differential is an improved differential for limiting the slip of wheels, namely a differential similar to the differential which is allowed to have a certain range of rotation speed difference of driving wheels so as to ensure the normal running performance of turning and the like, but can limit the differential not to output all power to the slipping or suspended wheels when one driving wheel slips or is suspended, thereby being beneficial to the control of the vehicle during the escaping and the violent driving. For example, when a wheel of a vehicle falls into a pit, the wheel has no friction, the ground-contacting wheel has a great resistance, and the common differential mechanism can feed all power back to the low-friction wheel. The wheels falling into the pits will rotate continuously, while the ground-engaging wheels are completely inactive, so that the wheels cannot run, which would not be the case if the vehicle were equipped with a limited slip differential. Current limited slip differentials have been locked using electronically controlled multiplate clutches, as well as through purely mechanical worm gears.
Disclosure of Invention
The invention provides a limited slip differential, which has the following specific technical scheme.
The limited slip differential consists of an internal gear pair consisting of a shell, a swing gear A and an output gear A, an internal gear pair consisting of a swing gear B and an output gear B, at least two A-type intermediate gears, at least two B-type intermediate gears and at least two friction plates; the radial direction of each A-type intermediate gear is fixed with the shell, the rotation axis is parallel to the rotation axis of the shell, each A-type intermediate gear is meshed with at least one B-type intermediate gear, the gear pair gear ratio of each A-type intermediate gear and each B-type intermediate gear is the same, the eccentric shafts with the axes parallel to the rotation axis are arranged on each A-type intermediate gear, the distances between the eccentric shafts on each A-type intermediate gear and the rotation axes of the gears are the same, the phases of the eccentric shafts on all A-type intermediate gears are the same, the eccentric shafts on each A-type intermediate gear are radially fixed with the swing gear A respectively, the output gear A is coaxial with the rotation axis of the shell, and a friction plate is arranged between each A-type intermediate gear and the swing gear A or between the output gear A-type intermediate gear and the shell; The radial direction of each B-type intermediate gear is fixed with the shell, the rotation axis is parallel to the rotation axis of the shell, each B-type intermediate gear is meshed with at least one A-type intermediate gear, the eccentric shafts with the axes parallel to the rotation axis are arranged on each B-type intermediate gear, the distances between the eccentric shafts on each B-type intermediate gear and the rotation axis are the same, the phases of the eccentric shafts on all B-type intermediate gears are the same, the eccentric shafts on each B-type intermediate gear are radially fixed with the swinging gear B respectively, the output gear B is coaxial with the rotation axis of the shell, and a friction plate is arranged between each B-type intermediate gear and the swinging gear B or between each B-type intermediate gear and the shell. The description of the above spatial positional relationship definition is a more rigorous description method for defining direct or indirect connection and contact between parts, and a person skilled in the art can understand the connection relationship between parts and the overall structure of the technical solution of the present invention according to the description of the above spatial positional relationship; the shell can be one part or a member composed of a plurality of parts, and the shell member does not need to completely wrap all the parts, and only needs to enable the parts to meet the spatial position relation and the mechanical connection relation; The explanation of the more precise spatial relationship of the radial fixing of the type a and type B intermediate gears with respect to the housing is that the rotation axis of each intermediate gear is fixed at a point through the radial section of the housing, or that the radial fixing relationship between the oscillating gear a and the eccentric shafts of all type a intermediate gears is also in accordance with the above description, because the rotation axis between the intermediate gears and the housing, which requires bearings or oil lubrication, is limited to a small fixing area through the radial section of one housing, with the rotation axis being free of play, the relationship between the housing and all intermediate gears is understood to be the relationship between the planet carrier and the planet gears; The A-type intermediate gear and the B-type intermediate gear can be the same gears or gears with different tooth numbers and can form an external gear pair, the spatial position relationship that the eccentric shafts on all the A-type intermediate gears have the same phase can be understood that the axial lead of the eccentric shaft of each A-type intermediate gear of any two A-type intermediate gears is always parallel to the plane determined by the rotation axial lead of the gears, the swing gear A synchronously revolves with the rotation of each A-type intermediate gear by taking the rotation axial lead of the shell as the axis during differential speed, the swing gear B synchronously revolves with the rotation of each B-type intermediate gear by taking the rotation axial lead of the shell as the axis during differential speed operation, and the torque is input from the shell, The external force is input through what structure and output through what structure are respectively output from the output gear A and the output gear B, but the external force is output through a common gear or a rotating shaft, the parts or components of the differential can be reprocessed with gears or the spline of a connecting shaft, and the friction plate is a part for increasing the friction force between the parts.
According to the limited slip differential, the shell rotates under the action of external force to drive each A-type intermediate gear and each B-type intermediate gear to revolve along with the shell around the shell rotation shaft, the eccentric shaft on each A-type intermediate gear drives the swing gear A to rotate along with the shell, the swing gear A drives the output gear A to rotate, the eccentric shaft on each B-type intermediate gear drives the swing gear B to rotate along with the shell, the swing gear B drives the output gear B to rotate, and the output gear A and the output gear B respectively output and rotate; when the rotation speeds of the output gear A and the output gear B are the same, all parts in the differential mechanism are static relative to the shell; When the output loads of the output gear A and the output gear B are different, the output gear A and the output gear B rotate relatively, namely the output gear A and the output gear B rotate relatively in opposite directions with the shell respectively, so that the swing gear A and the swing gear B revolve relatively to the shell relative to the rotation axis of the shell, the swing gear A and the swing gear B revolve relatively to the rotation axis of the shell to drive each A-type intermediate gear and each B-type intermediate gear to rotate relatively to opposite directions through the eccentric shaft, and the output gear A and the output gear B can only rotate relatively to the shell in opposite directions in a fixed rotation speed ratio relation due to the meshing of the A-type intermediate gears and the B-type intermediate gears. the above is the principle of the transmission relation of the rotational motion of the differential mechanism or the transmission relation of the torque and the realization of the differential output; further explaining the realization principle of the potential slip limiting mechanism of the differential of the invention, the number of teeth of the output gear A and the swing gear A determine the rotation speed ratio of the swing gear A driven by the rotation of the output gear A relative to the shell by taking the rotation axis of the shell as the axis, the revolution speed of the swing gear A is the same as the rotation speed of each A-type intermediate gear, the number of teeth of the output gear B and the swing gear B determine the rotation speed ratio of the swing gear B driven by the rotation of the output gear B relative to the shell relative to the rotation of the shell by taking the rotation axis of the shell as the axis, the revolution speed of the swing gear B is the same as the rotation speed of each B-type intermediate gear, When the two rotational speeds are relatively high, the internal load of the differential mechanism during the relative rotation of the output gear A and the output gear B is proportionally amplified according to the relative rotation rotational speeds due to the existence of friction force and the fluid resistance of lubricating oil, particularly the larger resistance caused by the friction movement of the friction plate between parts, meanwhile, the internal load of the differential mechanism is also increased at the meshing surface pressure between the output gear A and the swing gear A and between the output gear B and the swing gear B, the transmission resistance of the gear pair between the output gear A and the swing gear A and between the output gear B and the swing gear B is increased, the load of the relative rotation of the output gear A and the output gear B is further increased, The increase of the loads balances the external output load difference which causes the rotation speed difference of the output gear A and the output gear B, so that the output gear A and the output gear B tend to output at the same speed, namely the limited slip effect is achieved; Whether or not the lock is achieved in the case of slipping in particular, depending on the maximum value of the increase in the internal load of the differential, the relative lock between the output gear a and the output gear B can be achieved theoretically when the internal load of the differential caused by the relative torque or the relative rotational speed of the output gear a and the output gear B is equal to or greater than the torque input to the housing.
The gear pair formed by the swing gear A and the output gear A or the gear pair formed by the swing gear B and the output gear B is a cycloidal gear pair. The cycloidal gear pair comprises a cycloidal pin gear pair, when the cycloidal gear pair has fewer tooth differences, two gears can revolve around the rotation axis of the other gear for a plurality of circles correspondingly when rotating relatively, the resistance during rotation can be amplified, the cycloidal gear can select gears with fewer teeth, the bearing capacity of the gears can be increased in a limited space, in addition, the relation between the rotation resistance of gear engagement and the torque load can be adjusted by adjusting the tooth shape of the cycloidal gear, and the differential with different limited slip capacities can be implemented more favorably.
The limited slip differential is characterized by comprising at least 3A-type intermediate gears and at least 3B-type intermediate gears. The above 3A-type intermediate gears and the above 3B-type intermediate gears are provided with 3 eccentric shafts which are connected with the swing gear A and the swing gear B, so that the stability of revolution of the swing gear around the rotation axis of the shell is facilitated, and the 3 eccentric shafts are also more favorable for the torque load capacity of the shell to rotate so as to drive the swing gear and the shell to synchronously rotate.
The output gear a and the output gear B are external gears. At this time, the rotation of the output gear drives the swing gear in the gear pair to revolve in the direction opposite to the rotation direction of the output gear, which is that the gear transmission resistance between the output gear and the swing gear is larger, so that the differential lock is more beneficial to being applied to a limited slip differential, or the rotation resistance is larger than the input torque after the transmission torque is increased to a certain fixed value, and the gear is locked.
The output gear a and the output gear B are internal gears. At the moment, the rotation of the output gear drives the swing gear in the gear pair to revolve in the same direction as the rotation direction of the output gear, and at the moment, the gear transmission resistance between the output gear and the swing gear is smaller, so that the reduction of resistance and torque loss during differential output of the differential mechanism is facilitated.
The A-type intermediate gear and the B-type intermediate gear are bevel gears or worms. The gear pair formed by the bevel gears can generate axial stress when relatively rotating, and the axial stress is beneficial to increasing the friction pressure between the gear and other axial parts, namely increasing the rotation resistance of the gear; the worm belongs to a gear, and the gear pair formed by the worm and the worm generates axial stress when relatively rotating, the axial stress increases the friction force between the worm and the worm in the worm gear pair, increases the self-rotation resistance of the worm, and simultaneously, the axial stress is beneficial to increasing the friction pressure between the worm and other axial parts and also increases the self-rotation resistance of the worm; after the rotation resistance of the intermediate gear is increased to a certain fixed value, the meshing rotation resistance of the intermediate gear A and the intermediate gear B can be caused to exceed the torque which causes the relative rotation of the intermediate gear A and the intermediate gear B, so that the locking of the differential mechanism is realized.
The output gear a, the output gear B, the swing gear a, and the swing gear B are fixed in the axial direction with respect to the housing, respectively. The spatial relationship fixed relative to the housing axis is further explained as that the component along the housing axis in the spatial position relationship with the housing remains unchanged, or a gap needs to be left between the radial or circumferential motion relative to the housing and the housing, or the component along the housing axis in the spatial position relationship between the rotating part and the housing is limited in a relatively small fixed range, such as that shown in the drawings, the housing limits the axial motion of the output gear a and the output gear B away from the housing from two ends, the space occupation of other parts in the housing limits the motion of the output gear a and the output gear B toward the center of the housing, the swing gear a and the swing gear B are similarly limited, no matter which axial fixing mode needs to keep a certain gap for motion influenced by the process, but the technical scheme of the invention can be supplemented by the fact that the technical scheme described in the first section is used in the spatial position description, because the technical scheme described in the first section is only limited in a certain range and all parts cannot be limited in the axial direction, the relative motion of the gear a certain limited range is limited in the axial direction, and the technical scheme described in the relative position of the first section is further limited by the technical scheme is further described as a further condition that the technical scheme is added.
The A-type intermediate gear and the B-type intermediate gear are axially fixed relative to the housing. The spatial relationship fixed relative to the axial direction of the housing is further explained as that the component along the axial direction of the housing in the spatial position relationship with the housing remains unchanged, or a gap is required to be reserved for rotation due to the need of bearing or oil lubrication between the circumferential motion relative to the housing and the housing, the component along the axial direction of the housing in the spatial position relationship between the rotating part and the housing is limited in a relatively small fixed range and is also a fixed form, no matter which axial fixing mode is influenced by the process, a certain movable range can be provided, but the technical scheme of the invention can be supplemented by the term of 'fixing' in the spatial position description, so that the technical scheme of the invention can be understood by a person in the field, and the technical scheme of the invention can be further emphasized by the fact that as long as the technical scheme of the first section is satisfied and all parts are not possible to be infinitely long in the axial direction, the gear is limited in a certain relative axial moving range, so that the connecting relationship can be satisfied, the limitation is that the technical scheme of the first section is already defined as an implicit limitation of the filling condition, no matter of the technical scheme of the first section is provided with a relatively large axial moving space for the intermediate gear, and the axial displacement of the intermediate gear is emphasized by the axial displacement of the further limited scheme of the axial direction is emphasized when the axial displacement of the axial scheme of the intermediate gear is selected and limited in the axial limitation is increased by the axial limitation scheme of the axial limitation.
The differential case further includes a gear or spline or screw hole for mechanical connection with the torque input part; the output gear A and the output gear B respectively further comprise gears or splines which are used for mechanically connecting with a torque output load. In the description of the above technical solutions of the present invention, the purpose is to describe the structure and the mechanical transmission relation of the differential mechanism, the mechanical connection structure of the differential mechanism and the external parts is not a part of the structure of the differential mechanism for achieving the differential effect, so that the differential mechanism is not described in the technical solutions, but obviously, when the differential mechanism works, the differential mechanism and all parts without power sources need to be mechanically connected with the external, when the differential mechanism is applied to equipment, the input of the torque of the differential mechanism can be that a gear fixed with the circumference of the casing is arranged outside the casing, the gear is meshed with the torque input gear, or that the casing is connected with the input shaft through a spline and coaxially and synchronously rotates; the torque output can be realized by selecting an output gear A and an output gear B which are respectively connected with two output shafts through splines and coaxially and synchronously rotate, or by selecting gears meshed with external torque loads on the output gear A and the output gear B.
The differential mechanism can realize the distribution setting of torque output by setting the gear ratio of the A-type intermediate gear and the B-type intermediate gear; the distribution setting of torque output can be realized through the difference between the gear ratio of the swing gear A and the output gear A and the gear ratio of the swing gear B and the output gear B, which is an important progress advantage of the differential device, the limitation of the range of adjusting torque distribution of various differentials in the prior art is solved through setting the gear ratio of the adjustable output torque distribution at the two positions, the processing difficulty and the processing cost of the modeling of the differential designed for adjusting the torque distribution are reduced compared with the prior art, and the torque bearing capacity of the differential with the same size is improved compared with certain differentials in the prior art.
The differential is mainly used for outputting engine power of a vehicle to wheels after passing through a gearbox, when the differential is used as a central differential, the gearbox outputs torque to a differential shell, an output gear A and an output gear B respectively output torque to front and rear differentials, when the differential is used as a front differential or a rear differential, the torque output by the central differential is output to the differential shell through a rotating shaft or a gear, and an output gear A and an output gear B of the differential respectively output torque to left and right wheels.
The load mentioned in the technical scheme of the invention is mechanical load, which refers to the resistance generated by the parts to be driven or other parts to be driven to rotate during rotation, and when the differential mechanism is applied to an automobile, the load refers to the resistance born by the differential mechanism which is required to drive the rotation axle and the wheels to rotate; torque is sometimes referred to as torque when a rotating part is transmitting rotation, and is used in the description of the technical solution of the present invention or is described in a logical or relational manner.
Drawings
Fig. 1 is a schematic view (cross-sectional view) of the limited slip differential of embodiment 1.
FIG. 2 is an exploded view of the limited slip differential of embodiment 1.
Fig. 3 is a perspective view of the limited slip differential of embodiment 1.
In the figure: 1, a shell; 2, a middle gear; 3, type b intermediate gear; 4, swinging the gear A;5, swinging the gear B;6, outputting a gear A;7, outputting a gear B;8, friction plate.
Detailed Description
In the embodiment 1, as shown in fig. 1-3, the selected a-type intermediate gear is 3 identical involute spur gears, the B-type intermediate gear is also 3 identical involute spur gears, the teeth numbers of the a-type intermediate gear and the B-type intermediate gear are all equal, 3 a-type intermediate gears and 3B-type intermediate gears are mutually meshed to form 3 gear pairs, the oscillating gear a and the output gear a are respectively provided with a pair of cycloidal internal gear pairs with the teeth difference of 2, wherein the output gear a is an external gear, both ends of the a-type intermediate gear are respectively provided with a shaft and are respectively provided with an eccentric shaft which axially extends out, the eccentric shafts on the 3 a-type intermediate gears are respectively inserted into shaft holes on the end faces of the oscillating gear a, the oscillating gear B and the output gear B are respectively provided with a pair of cycloidal internal gear pairs which are respectively identical with the tooth shapes of the oscillating gear a and the output gear a, both ends of the B-type intermediate gear are respectively provided with a shaft and are respectively provided with an eccentric shaft which axially extends out, the 3B-type intermediate gear a is respectively inserted into shaft holes on the end faces of the oscillating gear B, the output gear B is provided with a housing, and the output gear B is provided with a base plate and a shell is respectively provided with a shaft hole which is respectively connected with the two end faces of the intermediate gear, and the intermediate gear B is provided with a friction plate, and the shell is arranged between the two shell parts, as shown in the two shell parts are respectively, and the shell parts are arranged.
Claims (10)
1. A limited slip differential, characterized by: the device comprises an internal gear pair consisting of a shell, a swing gear A and an output gear A, an internal gear pair consisting of a swing gear B and an output gear B, at least two A-type intermediate gears, at least two B-type intermediate gears and at least two friction plates; the radial direction of each A-type intermediate gear is fixed with the shell, the rotation axis is parallel to the rotation axis of the shell, each A-type intermediate gear is meshed with at least one B-type intermediate gear, the gear pair gear ratio of each A-type intermediate gear and each B-type intermediate gear is the same, the eccentric shafts with the axes parallel to the rotation axis are arranged on each A-type intermediate gear, the distances between the eccentric shafts on each A-type intermediate gear and the rotation axes of the gears are the same, the phases of the eccentric shafts on all A-type intermediate gears are the same, the eccentric shafts on each A-type intermediate gear are radially fixed with the swing gear A respectively, the output gear A is coaxial with the rotation axis of the shell, and a friction plate is arranged between each A-type intermediate gear and the swing gear A or between the output gear A-type intermediate gear and the shell; the radial direction of each B-type intermediate gear is fixed with the shell, the rotation axis is parallel to the rotation axis of the shell, each B-type intermediate gear is meshed with at least one A-type intermediate gear, the eccentric shafts with the axes parallel to the rotation axis are arranged on each B-type intermediate gear, the distances between the eccentric shafts on each B-type intermediate gear and the rotation axis are the same, the phases of the eccentric shafts on all B-type intermediate gears are the same, the eccentric shafts on each B-type intermediate gear are radially fixed with the swinging gear B respectively, the output gear B is coaxial with the rotation axis of the shell, and a friction plate is arranged between each B-type intermediate gear and the swinging gear B or between each B-type intermediate gear and the shell.
2. A limited slip differential according to claim 1, wherein: the shell rotates under external force to drive each A-type intermediate gear and each B-type intermediate gear to revolve along with the shell around the shell rotation shaft, an eccentric shaft on each A-type intermediate gear drives a swing gear A to rotate along with the shell, the swing gear A drives an output gear A to rotate, an eccentric shaft on each B-type intermediate gear drives a swing gear B to rotate along with the shell, the swing gear B drives the output gear B to rotate, and the output gear A and the output gear B respectively output and rotate; when the rotation speeds of the output gear A and the output gear B are the same, all parts in the differential mechanism are static relative to the shell; when the output loads of the output gear A and the output gear B are different, the output gear A and the output gear B rotate relatively, namely the output gear A and the output gear B rotate relatively in opposite directions with the shell respectively, so that the swing gear A and the swing gear B revolve relatively to the shell relative to the rotation axis of the shell, the swing gear A and the swing gear B revolve relatively to the rotation axis of the shell to drive each A-type intermediate gear and each B-type intermediate gear to rotate relatively to opposite directions through the eccentric shaft, and the output gear A and the output gear B can only rotate relatively to the shell in opposite directions in a fixed rotation speed ratio relation due to the meshing of the A-type intermediate gears and the B-type intermediate gears.
3. A limited slip differential according to claim 1, wherein: the gear pair formed by the swing gear A and the output gear A or the gear pair formed by the swing gear B and the output gear B is a cycloidal gear pair.
4. A limited slip differential according to claim 1, wherein: the differential includes at least 3 type a intermediate gears and at least 3 type B intermediate gears.
5. A limited slip differential according to claim 1, wherein: the output gear A and the output gear B are external tooth gears.
6. A limited slip differential according to claim 1, wherein: the output gear A and the output gear B are internal tooth gears.
7. A limited slip differential according to claim 1, wherein: the A-type intermediate gear and the B-type intermediate gear are bevel gears or worms.
8. A limited slip differential according to claim 1, wherein: the output gear A, the output gear B, the swing gear A and the swing gear B are respectively axially fixed relative to the shell.
9. A limited slip differential according to claim 1, wherein: the A-type intermediate gear and the B-type intermediate gear are axially fixed relative to the shell.
10. A limited slip differential according to claim 1, wherein: the differential case also includes a gear or spline or screw hole for mechanical connection with the torque input part; the output gear A and the output gear B respectively further comprise gears or splines which are used for mechanically connecting with a torque output load.
Priority Applications (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710215142.3A CN106838202B (en) | 2017-04-02 | 2017-04-02 | Limited slip differential |
| EP18781709.3A EP3608558B1 (en) | 2017-04-02 | 2018-03-31 | Cycloidal differential |
| US16/496,891 US10920865B2 (en) | 2017-04-02 | 2018-03-31 | Differential and cycloidal differential |
| PCT/CN2018/081481 WO2018184506A1 (en) | 2017-04-02 | 2018-03-31 | Differential and cycloidal differential |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710215142.3A CN106838202B (en) | 2017-04-02 | 2017-04-02 | Limited slip differential |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106838202A CN106838202A (en) | 2017-06-13 |
| CN106838202B true CN106838202B (en) | 2024-07-23 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710215142.3A Active CN106838202B (en) | 2017-04-02 | 2017-04-02 | Limited slip differential |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| US10920865B2 (en) | 2017-04-02 | 2021-02-16 | Zilong Ling | Differential and cycloidal differential |
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|---|---|---|---|---|
| CN207111876U (en) * | 2017-04-02 | 2018-03-16 | 凌子龙 | A kind of limited-slip differential |
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| US9080659B2 (en) * | 2011-01-11 | 2015-07-14 | Jtekt Corporation | In-wheel motor driving device |
| CN201944224U (en) * | 2011-01-20 | 2011-08-24 | 史凯 | Antiskid differential of automobile |
| CN103791057A (en) * | 2014-02-11 | 2014-05-14 | 安宏亮 | Eccentric wheel limited slip differential |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN207111876U (en) * | 2017-04-02 | 2018-03-16 | 凌子龙 | A kind of limited-slip differential |
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| CN106838202A (en) | 2017-06-13 |
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