WO2008101371A1 - A kind of limited-slip differential with an asymmetric structure - Google Patents

A kind of limited-slip differential with an asymmetric structure Download PDF

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Publication number
WO2008101371A1
WO2008101371A1 PCT/CN2007/001353 CN2007001353W WO2008101371A1 WO 2008101371 A1 WO2008101371 A1 WO 2008101371A1 CN 2007001353 W CN2007001353 W CN 2007001353W WO 2008101371 A1 WO2008101371 A1 WO 2008101371A1
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WO
WIPO (PCT)
Prior art keywords
gear
differential
planet
annular gear
bore
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Application number
PCT/CN2007/001353
Other languages
French (fr)
Inventor
Hong Jiang
Xiaochun Wang
Original Assignee
Hong Jiang
Xiaochun Wang
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Filing date
Publication date
Application filed by Hong Jiang, Xiaochun Wang filed Critical Hong Jiang
Publication of WO2008101371A1 publication Critical patent/WO2008101371A1/en

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Classifications

    • 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
    • F16H48/28—Arrangements for suppressing or influencing the differential action, e.g. locking devices using self-locking gears or self-braking gears
    • F16H48/285—Arrangements for suppressing or influencing the differential action, e.g. locking devices using self-locking gears or self-braking gears with self-braking intermeshing gears having parallel axes and having worms or helical teeth
    • 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
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
    • F16H2048/104—Differential gearings with gears having orbital motion with orbital spur gears characterised by two ring gears
    • 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
    • F16H48/28—Arrangements for suppressing or influencing the differential action, e.g. locking devices using self-locking gears or self-braking gears

Definitions

  • the present invention relates to a kind of limited-slip differential used between either driving wheels or driving axles, particularly relates to a kind of limited-slip differential characterized by asymmetric structure and internal gearing in both sides.
  • preload frictional mechanism cannot adjust its performance in accordance with the input torque applied to the differential or the load on its output ends, so a certain preload friction torque may be not enough when the vehicle is heavily loaded, could cause power recycling when the vehicle is empty;
  • the adhesive coupling limits is the slip speed of the driving wheels, not the slip phenomenon, once a continuous slip between the tyre and ground occurs, a character similar to liquid friction will appear between the tyre and the ground, leading to the vehicle sideslip and out of control.
  • Torson differential is a kind of new limited-slip differential, the working principle of which is based upon the low transmission efficiency of spherical worm gearings, and the generated inner friction limits the slip of the driving wheels, having a character that the slip limit ability being proportional to the output torque of the gear box.
  • the basic torque distribution is equally distributed.
  • the torque distributed to the front axle will be too large and the driving wheel is always in a criticality of slip, not only the wear and tear of the front driving wheels is increased, but also the driving stability of the vehicle is damaged.
  • the Torson differential based upon spherical worm gears has the drawback of rather higher price.
  • the limited-slip differential Truetric (US5194054) used between both driving wheels and axles utilizes cylindrical gears with large helix angle to compose an epicyclic unit, with all the cylindrical gears being external gears, using the tip cylinder of the planet gears and end surface of side gears as friction surfaces to limit its differential motion, and its ability in slip limitation is proportional to the input torque.
  • the planetary gears are rather slender, thus several pairs of planetary gears evenly distributed around the sun gears are adopted to satisfy the requirement of the strength, the radial forces applied no sun gears will offset with each other, having no contribution to the limitation of its slip.
  • the designer used cylindrical gears with large helix angle to compose an epicyclic unit, utilizing the axial thrust generated in gear engagement process to push the ends of side gears against the end covers or the separate ring between the side gears to generate some additional friction moment to improve the ability in slip limitation.
  • Slender planetary gears tend deformation in heat treatment process, and slender and crossing bores in planet carrier are difficult in machining and case hardening, the cost in manufacture is rather high.
  • the object of present invention is to provide a kind of limited-slip differential with an asymmetric structure, which can be used between either driving wheels or driving axles, characterized by its output torque ratio between both output sides can basically meet required torque ratio if the friction between the components is not considered, being compact in structure, easer in maintenance and manufacture.
  • the scheme of present invention is a kind of limited-slip differential with an asymmetric structure, comprises of a differential case and a planetary carrier held within the differential case, wherein the differential also comprises of:
  • a first-side annular gear and a second-side annular gear located individually in the first and second ends of the differential case, as two output sides of the differential;
  • a first-side planet gear and a second-side planet gear individually located in the bores of the planet carrier, engages with each other, meanwhile the first-side planet gear also engages and only engages with the first-side annular gear, and the second-side planet gear also engages and only engages with the second-side annular gear;
  • the differential according to present invention is used between the driving wheels, the said first and second sides are respectively the right and left sides of the driving direction of the vehicle, while the differential according to present invention is used between the front and rear driving axles, the first and second sides are respectively the front and rear sides of the vehicle.
  • the third and forth bores are also machined in either the differential case or the planet carrier, the said first-side annular gear located in the third bore with sliding fit, and the second-side annular gear is located in the forth bore with sliding fit. Therefore, since either the first-side or second-side annular gear engages with only one corresponding planet gear, for each internal gear pair composed by one annular gear and one planet gear is asymmetric in structure, the tangential and radial force applied on the annular gear is asymmetric, cannot be balanced by other tangential and radial forces generated in engagement, the excircle of the annular gear will be squeezed closely onto the inner wall of the bore machined in either the differential case or planet carrier, therefore the excircle of the first-side annular gear and the inner wall of the third bore compose a pair of friction components. Similarly the excircle of the second-side annular gear and the inner wall of the forth bore also compose a pair of friction components.
  • the said differential also comprises two end covers fixed to both ends of the differential.
  • the differential case can be either separate from the planet carrier or integrate with the planet carrier.
  • the axial contact width between the first-side and second-side outer planet gears is larger than either the axial contact width between the first-side planet gear and first-side annular gear or the axial contact width between the second-side planet gear and second-side annular gear.
  • the said first-side and second-side planet gears can adopt a smaller pressure angle between 14.5 and 17.5 degrees or smaller addendum coefficient between 0.8 and 0.9.
  • the said first-side and second-side annular gears can adopt a smaller pressure angle between 14.5 and 17.5 degrees or smaller addendum coefficient between 0.8 and 0.9.
  • the choice of the number of teeth in the gears in epicyclic train should meet required distribution of output torque between output sides, that means the ratio between the number of teeth in annular gears is close to required torque distribution ratio, while the number of teeth and modification coefficient in planet gears only need to meet the mounting condition, i.e. the axes of both annular gears coincide with each other, and no interference occurs.
  • the differential according to present invention can be used in a final reduction gear, the said first-side and second-side annular gears have the same number of teeth.
  • the differential according to present invention can used in a branch box, the input power is applied to the differential case, the first-side annular gear is connected to the front axle through a front driving shaft, and the second-side annular gear is connected to the rear axle through a rear driving shaft.
  • the number of teeth in the first-side annular gear is less than that in the second-side annular gear.
  • the first-side planet gear can extend form the first-side annular gear to second-side annular gear along axial direction, and contact the second-side planet gear in whole tooth width of the second-side planet gear.
  • the friction pairs composed of said tip cylinders of planet gears and the inner wall of the bores machined in planet carrier and the friction pairs composed of the excircles of annular gears and the inner wall of the bores machined in differential case or planet carrier will generate enough friction torque to restrict the slip of driving axles, and the normal pressure between friction pairs are proportional to the input torque of the differential.
  • the planet carrier of the differential transforms the input torque into the normal pressure on one side of the tip cylinder of the planet gears, and the normal pressure applied on each planet gear is balanced by a pair of tangent forces generated in the process of the planet gear engaging with both the annular gear and the other planet gear.
  • this normal pressure will generate a friction moment proportional to the input torque, which will directly lead to a bias in the distribution of the tangent force applied individually to each annular gear, making the component with a lower angular speed get larger torque to increase the input torque applied to the driving wheel or axle with higher adhesive force, and the component with higher angular speed get less torque to limit the slip of the driving wheel or the axle which is connected to it.
  • each annular gear according to present invention engages with only one planet gear, the tangential and radial force applied on the annular gear is asymmetric, cannot be balanced by other tangential and radial force generated in engagement process, thus the force must be balanced by the normal pressure of the inner wall of the bore in differential case or planet carrier applied on the annular gear. Once the slip occurs or the tendency of slip appears, this normal pressure will generate a friction moment proportional to the input torque, which will make the component with lower angular speed get part of the torque directly from the input end of the differential to increase the driving torque applied to the driving wheel or axle with higher adhesive force, and reduce the torque applied to the component with higher angular speed to get a further limitation to the slip of the driving wheel or axle connected to it.
  • FIG. 1 is a schematic section view of the differential used between driving wheels or forward rear axle and rear axle according to present invention
  • FIG. 2 is a schematic section view of the planet carrier in FIG. 1;
  • FIG. 3 is a right side view of the planet carrier of FIG. 2;
  • FIG. 4 is a schematic section view of the differential used between front and rear driving axles according to present invention;
  • FIG. 5 is a schematic section view of the planet carrier in FIG. 4;
  • FIG. 6 is a right side view of the planet carrier of FIG. 5;
  • FIG. 7 is a left side view of the planet carrier of FIG. 5.
  • the limited-slip differential with an asymmetric structure for the usage between driving wheels and axles comprises of a differential case 1 and planet carrier 6 which is fixed in the differential case 1, transforms the input torque to planet gears 4 and 5 and keeps the planet gears in position;
  • the first-side annular gear 2, second-side annular gear 3, first-side planet gar 4 which is in engagement with the first-side annular gear and second-side planet gear 5 which is in engagement with the first-side planet gear and the second-side annular gear 3 compose an epicyclic unit.
  • both the first-side planet gear 4 and second-side planet gear 5 have neither journals, nor any rolling bearings being fixed on them, but utilize the fit between the tip cylinder 41 of the first-side planet gear 4 and the first bore 61 to compose a sliding gearing to support the first-side planet gear, thus the tip cylinder 41 of the first-side gear 4 is used as the supporting surface of the first-side planet gear, being supported on the inner wall of the first bore 61, and the tip cylinder 41 of the first-side planet gear 4 and the inner wall of the first bore 61 machined in planet carrier 6 compose a friction pair components; similarly, the tip cylinder 51 of the second-side planet gear 5 is used as the supporting surface of planet gear 5, being supported on the inner wall of the second bore 62, and the tip cylinder of the second-side planet gear 5 and the inner wall of the second bore 62 machined in planet carrier 6 compose a friction pair components.
  • the planet carrier 6 of the differential transforms the input torque into the normal pressure on one side of the tip cylinder 41 of the first-side planet gear 4 and the normal pressure on one side of the tip cylinder 51 of the second-side planet 5, the normal pressure applied on the first-side planet gear 4 and second-side planet gear 5 are separately balanced by a pair of tangent and radial forces generated in the process of the planet gear engaging with either the first-side annular gear 2 or the second-side annular gear 3 and the engagement between planet gears.
  • this normal pressure will generate a friction torque proportional to the input moment, which will directly lead to a bias in the distribution of the tangent force the first-side planet gear 4 and second-side planet gear applied individually to the first-side annular gear 2 and second-side annular gear 3, making the component with a lower angular speed get larger torque to increase the input torque applied to the driving wheel or axle with higher adhesive force, and the component with higher angular speed get less torque to limit the slip of the driving wheel or the axle which is connected to it.
  • the differential according to present invention also comprises a pair of end covers 13 and 14 fixed to both ends of the differential case 1.
  • the third bore 11 and forth bore 12 are machined in differential case 1 or planet carrier 6, the said first-side annular gear 2 situated in the third bore 11 with sliding fit, and the said second-side annular gear 3 situated in the forth bore 12 with sliding fit.
  • first-side annular gear 2 or second-side annular gear 3 engages with only one planet gear, for each internal gear pair composed of an annular gear and a planet gear is asymmetric in structure, the tangential and radial force applied on the annular gear is also asymmetric, cannot be balanced by other tangential and radial force generated in engagement process, the excircle of the annular gear will be squeezed closely onto the inner wall of the bore machined in either the differential case 1 or planet carrier 6, therefore the excircle 21 of the first-side annular gear 2 and the inner wall of the third bore 11 compose a pair of friction components, similarly, the excircle 31 of the second-side annular gear 3 and the inner wall of the forth bore 12 also compose a pair of friction components.
  • the tangential and radial force applied on the annular gear is asymmetric, cannot be balanced by other tangential and radial force generated in engagement, thus the two forces must be balanced by the normal pressure of the inner wall of the bore 11 and 12 in differential case or planet carrier applied on the annular gears.
  • this normal pressure will generate a pair of friction moment proportional to the input torque, which will make the component with lower angular speed get part of the torque directly from the input end of the differential to increase the driving torque applied to the driving wheel or axle with higher adhesive force, and reduce the torque applied to the component with higher angular speed to get a further limitation to the slip of the driving wheel or axle connected to it.
  • the first-side annular gear 2 and second-side annular gear 3 are individually situated in the third bore 11 and forth bore 12 with sliding fit. Since there are no rolling bearings arranged in the differential according to present invention, the components are arranged close to each other, being characterized by compact structure and higher load capacity.
  • the said first-side annular gear 2, second-side annular gear 2, first-side planet gear 4 and second-side planet gear can be helical gears with the same helix angle or spur gears without helix angle, the helix angles at individual reference circles are the same or all equal to zero.
  • first-side planet gear 4 and second-side planet gear 5 have an inverse hand of helix, while the first-side planet gear 4 and first-side annular gear 2 have the same hand of helix, and the second-side planet gear 5 and second-side annular gear 3 have the same hand of helix.
  • the axial thrusts generated on the first-side planet gear 4 when it engages with the first-side annular gear 2 and second-side planet gear 5 can be basically balanced with each other, and the axial thrusts generated on the second-side planet gear 5 when it engages with the second-side annular gear and first-side planet gear 4 can also be basically balanced with each other, but the axial thrusts applied on the first-side annular gear 2 and second-side annular gear 3 will generate normal pressure proportional to the input torque between the first-side annular gear 2, second-side annular gear 3 and the end cover 13, 14 or the ends 63, 64 of the planet carrier.
  • the friction pairs composed of the tip cylinder 41 of the first-side planet gear 4 and the first bore 61 machined in planet carrier 6, the tip cylinder 51 of the second-side planet gear and the second bore 62 machined in planet carrier 6, the excircles of the first-side and second-side annular gears and the third and forth bores 11 and 12, and the end planes of the first-side and second-side annular gears 2 and 3 and the end covers 13 and 14 or the ends 63 and 64 of the planet carrier 6 under the effect of input torque can generate enough friction moment to limit the slip of a certain driving wheel connected to some axle. Since the normal pressure between friction pair components is proportional to the input torque, its slip-limit ability is proportional to the input torque.
  • the differential case 1 and planet carrier 6 can be integrated into one component.
  • the differential case and planet carrier can be separately manufactured and fixed together.
  • the axial contact width between the first-side planet gear 4 and second-side planet gear 5 is larger then the axial contact width either between the first-side planet gear 4 and first-side annular gear 2 or the contact width between the second-side planet gear 5 and second-side annular gear 3.
  • the choice of the number of teeth in the gears in epicyclic train should meet required distribution of output torque between output sides, that means the ratio between the number of teeth in the first-side annular gear and second-side annular gear is close to required torque distribution ratio, while the number of teeth and modification coefficient in planet gears only need to meet the mounting condition, i.e. the axes of both annular gears coincide with each other, and no interference occurs.
  • the tooth width of planet gears are increased in design process, and smaller pressure angle between 14.5 and 17.5 degrees or smaller addendum coefficient between 0.8 and 0.9 can be adopted.
  • the limited-sip differential according to present invention is to be used in a final reduction gear to distribute power to left and right driving wheels.
  • the first and second sides are corresponding respectively to the right and left sides of driving direction of the vehicle.
  • the input power (which is not illustrated in figure 1) applies to differential case 1, and required theoretical torque distribution is 1 :1, therefore the number of teeth in the first-side annular gear 2 (the right-side annular gear) and second-side annular gears 3 (the left-side annular gear) is the same and equal to 28, while the number of teeth in the first-side planet gear 4 (the right-side planet gear) and second-side planet gear (the left-side planet gear) is the same and equal to 14 and all annular and planet gears are spur gears.
  • a 20 degree pressure and addendum coefficient of 0.9 are adopted to get a larger tip width.
  • the differential is situated in a branch box, the input power is applied to the differential case, the first side annular gear 2 is connected to the front axle through a front driving shaft, and the second side annular gear 3 is connected to the rear axle through a rear driving shaft.
  • the first and second sides are respectively corresponding to the front and rear sides of the vehicle.
  • the required theoretical torque ratio is 1:1.5, thus the number of teeth in the first-side annular gear 2 (the front-side annular gear) is chosen to be 22, and the number of teeth in the second-side annular gear 3 (the rear-side annular gear) is 33, the number of teeth in the first-side planet gear 4 (the front-side planet gear) is 13, and the number of teeth in the second-side planet gear 5 (the rear-side planet gear) is 14, the theoretical torque distribution ratio coincides with the requirement.
  • the said first-side planet gear 4 can extend form the first-side annular gear 2 to second-side annular gear 3 along axial direction, and contact the second-side planet gear 5 in whole tooth width of the second-side planet gear 5, so that the contact width " between two external planet gears is increased, and the contact strength is reduced.
  • Some angular modification is used in planet gears to meet required centerline distance.
  • a normal pressure angle of 20 degrees is used for planet and annular gears.
  • the addendum coefficient is chosen to be 0.8, so that a wider tip width and larger supporting area can be obtained, and the wear and tear in the tip cylinders 41 and 51 and the first and second bores 61 and 62 can be decreased.
  • All the gears used in the differential are spur gears, and the range of output torque ratio between the first-side annular gear 2 and second-side annular gear 3 is between 1 :4.8 and 2.13 : 1 , a rather high ability in slip limitation is obtained, meanwhile on power recycling will occur.

Abstract

A kind of limited-slip differential with an asymmetric structure comprises of a differential case (1); a planet carrier (6) fixed in it; first-side and second-side annular gears (2, 3); first-side and second-side planet gears (4, 5) situated in the planet carrier (6) and engaging with each other, the first-side annular gear (2) engaging and only engaging with first-side planet gear (4), the second-side annular gear (3) engaging and only engaging with second-side planet gear (5); a first bore (61) machined in planet carrier (6), the first-side planet gear (4) situated in the first bore (61) with sliding fit; and a second bore (62) machined in planet carrier (6), the second-side planet gear (5) situated in the second bore (62) with sliding fit. The ability in slip limitation of limited-slip differential according to present invention is proportional to input torque applied to the differential.

Description

A KIND OF LIMITED-SLIP DIFFERENTIAL WITH AN ASYMMETRIC STRUCTURE
FIELD OF THE INVENTION
The present invention relates to a kind of limited-slip differential used between either driving wheels or driving axles, particularly relates to a kind of limited-slip differential characterized by asymmetric structure and internal gearing in both sides.
BACKGROND ART OF THE INVENTION
In order to improve off-road performance and crossing ability, many off-road utility vehicles, off-road trucks and engineering vehicles adopt different kinds of limited-slip differential between driving wheels and/or multi-axle drive. In order to distribute the power to every driving axle and at the same time accommodate the difference in average rolling distance of driving wheels when the vehicle drives on uneven road or turns, differentials are widely adopted between driving axles. Since the load on driving axles differs from each other, the torque distributed to each axle by the differential is required to be different in accordance with the load, so that the adhesion on each driving wheel can be utilized to the best, therefore various differentials involving different kind of mechanism for slip limitation between driving wheels and/or inter-axle differentials composed of epicyclic unit involving sun gear, planet and annular gears are commonly adopted, utilize different kinds of slip limitation mechanism to limit the slip of one driving wheel and the difference between the number of teeth in the sun and annular gears to get an unequal distribution of the output torque from both sides of the differential. However, the vehicle equipped with general satellite differentials may occasionally lose its traction if the adhesion, on one driving wheel abruptly drops when the vehicle drives on harsh road surface. In order to avoid this phenomenon, some off-road vehicle is equipped with toothed clutches between front and rear driving axles instead of differential, by means of the operation of the clutch to control whether the power applies to front or rear driving axles. The problem of this kind of layout is that once the vehicle drives back to hard ground and the power to the auxiliary driving axle is not disconnected on time, sever power circulation will occur, leading to increased fuel consumption and rapidly increased tyre wear and tear, meanwhile the increased load applied on the transmission system will greatly shorten its service life, maybe leading to an abrupt break in the transmission system.
Various limited-slip differentials for driving wheels are available, their working characteristics can be roughly divided into two families of speed sensitive and torque sensitive. Except for the limited-slip differential with fluctuating gear ratio that belongs to torque sensitive family and that based on the principle of overriding clutch that belongs to speed sensitive family, the others generally have complicated structure. However, the limited-slip differential with fluctuating gear ratio may generate some vibration in case one of the driving wheel slips at a high speed, being not suitable for limousine cars and SUV, while the smoothness of overdriving clutches is neither good enough. For constant multi-axle drive vehicles, to improve the crossing ability, some preload mechanism or multi-plate clutch dipped in some special adhesive oil are added to inter-axle differential to limit its slip. However, these slip limitation mechanisms are not only complicated in structure, larger in volume, heavier and higher in coast, but also present some drawbacks in their performance: preload frictional mechanism cannot adjust its performance in accordance with the input torque applied to the differential or the load on its output ends, so a certain preload friction torque may be not enough when the vehicle is heavily loaded, could cause power recycling when the vehicle is empty; what the adhesive coupling limits is the slip speed of the driving wheels, not the slip phenomenon, once a continuous slip between the tyre and ground occurs, a character similar to liquid friction will appear between the tyre and the ground, leading to the vehicle sideslip and out of control.
Torson differential is a kind of new limited-slip differential, the working principle of which is based upon the low transmission efficiency of spherical worm gearings, and the generated inner friction limits the slip of the driving wheels, having a character that the slip limit ability being proportional to the output torque of the gear box. However, without considering the inner friction of Torson differentials, the basic torque distribution is equally distributed. For those vehicles such as heavy-duty cross-country trucks, there is a great difference in the load distributed to front and rear driving axles. In this case, the torque distributed to the front axle will be too large and the driving wheel is always in a criticality of slip, not only the wear and tear of the front driving wheels is increased, but also the driving stability of the vehicle is damaged. Meanwhile the Torson differential based upon spherical worm gears has the drawback of rather higher price.
The limited-slip differential Truetric (US5194054) used between both driving wheels and axles utilizes cylindrical gears with large helix angle to compose an epicyclic unit, with all the cylindrical gears being external gears, using the tip cylinder of the planet gears and end surface of side gears as friction surfaces to limit its differential motion, and its ability in slip limitation is proportional to the input torque. Limited by its structure, the planetary gears are rather slender, thus several pairs of planetary gears evenly distributed around the sun gears are adopted to satisfy the requirement of the strength, the radial forces applied no sun gears will offset with each other, having no contribution to the limitation of its slip. In order to enhance slip-limitation ability, the designer used cylindrical gears with large helix angle to compose an epicyclic unit, utilizing the axial thrust generated in gear engagement process to push the ends of side gears against the end covers or the separate ring between the side gears to generate some additional friction moment to improve the ability in slip limitation. Slender planetary gears tend deformation in heat treatment process, and slender and crossing bores in planet carrier are difficult in machining and case hardening, the cost in manufacture is rather high.
SUMMARY OF THE INVENTION
The object of present invention is to provide a kind of limited-slip differential with an asymmetric structure, which can be used between either driving wheels or driving axles, characterized by its output torque ratio between both output sides can basically meet required torque ratio if the friction between the components is not considered, being compact in structure, easer in maintenance and manufacture.
To realize the object, the scheme of present invention is a kind of limited-slip differential with an asymmetric structure, comprises of a differential case and a planetary carrier held within the differential case, wherein the differential also comprises of:
A first-side annular gear and a second-side annular gear, located individually in the first and second ends of the differential case, as two output sides of the differential; A first-side planet gear and a second-side planet gear, individually located in the bores of the planet carrier, engages with each other, meanwhile the first-side planet gear also engages and only engages with the first-side annular gear, and the second-side planet gear also engages and only engages with the second-side annular gear;
A first bore machined in the planet carrier, and the said first-side planet gear located in the bore with sliding fit, with its tip cylinder being utilized as the supporting surface, being supported on the inner wall of the first bore, and the tip cylinder of the first-side planet gear and the inner wall of the first bore compose a pair of friction components;
A second bore machined in the planet carrier, and the said second-side planet gear located in the bore with a sliding fit, with its tip cylinder being utilized as the supporting surface, being supported on the inner wall of the second bore, and the tip cylinder of the second-side planet gear and the inner wall of the second bore compose a pair of fictional components;
For present invention, if the differential according to present invention is used between the driving wheels, the said first and second sides are respectively the right and left sides of the driving direction of the vehicle, while the differential according to present invention is used between the front and rear driving axles, the first and second sides are respectively the front and rear sides of the vehicle.
For present invention, the third and forth bores are also machined in either the differential case or the planet carrier, the said first-side annular gear located in the third bore with sliding fit, and the second-side annular gear is located in the forth bore with sliding fit. Therefore, since either the first-side or second-side annular gear engages with only one corresponding planet gear, for each internal gear pair composed by one annular gear and one planet gear is asymmetric in structure, the tangential and radial force applied on the annular gear is asymmetric, cannot be balanced by other tangential and radial forces generated in engagement, the excircle of the annular gear will be squeezed closely onto the inner wall of the bore machined in either the differential case or planet carrier, therefore the excircle of the first-side annular gear and the inner wall of the third bore compose a pair of friction components. Similarly the excircle of the second-side annular gear and the inner wall of the forth bore also compose a pair of friction components.
For present invention, the said differential also comprises two end covers fixed to both ends of the differential.
For present invention, the differential case can be either separate from the planet carrier or integrate with the planet carrier.
For present invention, in order to reduce the contact stress between tooth franks, the axial contact width between the first-side and second-side outer planet gears is larger than either the axial contact width between the first-side planet gear and first-side annular gear or the axial contact width between the second-side planet gear and second-side annular gear.
For present invention, the said first-side and second-side planet gears can adopt a smaller pressure angle between 14.5 and 17.5 degrees or smaller addendum coefficient between 0.8 and 0.9. For present invention, the said first-side and second-side annular gears can adopt a smaller pressure angle between 14.5 and 17.5 degrees or smaller addendum coefficient between 0.8 and 0.9.
For present invention, the choice of the number of teeth in the gears in epicyclic train should meet required distribution of output torque between output sides, that means the ratio between the number of teeth in annular gears is close to required torque distribution ratio, while the number of teeth and modification coefficient in planet gears only need to meet the mounting condition, i.e. the axes of both annular gears coincide with each other, and no interference occurs.
As one preferred embodiment, the differential according to present invention can be used in a final reduction gear, the said first-side and second-side annular gears have the same number of teeth.
As the other preferred embodiment, the differential according to present invention can used in a branch box, the input power is applied to the differential case, the first-side annular gear is connected to the front axle through a front driving shaft, and the second-side annular gear is connected to the rear axle through a rear driving shaft. The number of teeth in the first-side annular gear is less than that in the second-side annular gear. For this embodiment, on the premise that no interference occurs, the first-side planet gear can extend form the first-side annular gear to second-side annular gear along axial direction, and contact the second-side planet gear in whole tooth width of the second-side planet gear. For present invention, under the input torque applied to the differential, the friction pairs composed of said tip cylinders of planet gears and the inner wall of the bores machined in planet carrier and the friction pairs composed of the excircles of annular gears and the inner wall of the bores machined in differential case or planet carrier will generate enough friction torque to restrict the slip of driving axles, and the normal pressure between friction pairs are proportional to the input torque of the differential.
During the working process of the differential according to present invention, the planet carrier of the differential transforms the input torque into the normal pressure on one side of the tip cylinder of the planet gears, and the normal pressure applied on each planet gear is balanced by a pair of tangent forces generated in the process of the planet gear engaging with both the annular gear and the other planet gear. Once the slip occurs or the tendency of slip appears, this normal pressure will generate a friction moment proportional to the input torque, which will directly lead to a bias in the distribution of the tangent force applied individually to each annular gear, making the component with a lower angular speed get larger torque to increase the input torque applied to the driving wheel or axle with higher adhesive force, and the component with higher angular speed get less torque to limit the slip of the driving wheel or the axle which is connected to it.
Since each annular gear according to present invention engages with only one planet gear, the tangential and radial force applied on the annular gear is asymmetric, cannot be balanced by other tangential and radial force generated in engagement process, thus the force must be balanced by the normal pressure of the inner wall of the bore in differential case or planet carrier applied on the annular gear. Once the slip occurs or the tendency of slip appears, this normal pressure will generate a friction moment proportional to the input torque, which will make the component with lower angular speed get part of the torque directly from the input end of the differential to increase the driving torque applied to the driving wheel or axle with higher adhesive force, and reduce the torque applied to the component with higher angular speed to get a further limitation to the slip of the driving wheel or axle connected to it.
Since either the planet gears or annular gear according to present invention are arranged in corresponding bores with sliding fit, no rolling bearings being adopted, the components are arranged close to each other, being characterized by compact structure and higher load capacity. Since the normal pressure between all friction pairs is proportional to the input torque, provided the design parameters are reasonable, neither the situation of the slip-limit ability being not sufficient for a heavily loaded vehicle, nor the phenomenon of power recycling for empty one will occur.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a schematic section view of the differential used between driving wheels or forward rear axle and rear axle according to present invention;
FIG. 2 is a schematic section view of the planet carrier in FIG. 1;
FIG. 3 is a right side view of the planet carrier of FIG. 2; FIG. 4 is a schematic section view of the differential used between front and rear driving axles according to present invention;
FIG. 5 is a schematic section view of the planet carrier in FIG. 4;
FIG. 6 is a right side view of the planet carrier of FIG. 5;
FIG. 7 is a left side view of the planet carrier of FIG. 5.
DESCRIPTION OF THE PREFERRED EMBODIMENT
As illustrated in figures 1 to 7, the limited-slip differential with an asymmetric structure for the usage between driving wheels and axles according to present invention comprises of a differential case 1 and planet carrier 6 which is fixed in the differential case 1, transforms the input torque to planet gears 4 and 5 and keeps the planet gears in position;
A first-side annular gear 2 and a second-side annular gear 3 individually located in the first and second sides of the differential case 1 as both power output sides;
A first-side planet gear 4 and a second-side planet gear 5 located in the planet carrier 6 which is fixed in the differential case 1, with both planet gears in engagement with each other, the first-side annular gear 2 engages and only engages with the first-side planet gear 4, and the second-side annular gear 3 engages and only engages with the second-side planet gear 5;
A first bore 61 machined in the planet carrier 6, the said first-side planet gear 4 located in the first bore 61 with sliding fit, with its tip cylinder 41 being utilized as the supporting surface of the planet gear 4, being supported on the inner wall of the first bore 61, and the tip cylinder 41 of the first-side planet gear 4 and the inner wall of the first bore 61 compose a pair of friction components;
A second bore 62 machined in the planet carrier 6, the said second-side planet gear 5 located in the second bore 62 with sliding fit, with its tip cylinder 51 being utilized as the supporting surface of the planet gear 5, being supported on the inner wall of the first bore 62, and the tip cylinder 51 of the second side planet gear 5 and the inner wall of the second bore 62 compose a pair of frictional components. The first-side annular gear 2, second-side annular gear 3, first-side planet gar 4 which is in engagement with the first-side annular gear and second-side planet gear 5 which is in engagement with the first-side planet gear and the second-side annular gear 3 compose an epicyclic unit.
Since the said first-side planet gear 4 situated in the first bore with sliding fit, the second-side planet gear 5 situated in the second bore with sliding fit, both the first-side planet gear 4 and second-side planet gear 5 have neither journals, nor any rolling bearings being fixed on them, but utilize the fit between the tip cylinder 41 of the first-side planet gear 4 and the first bore 61 to compose a sliding gearing to support the first-side planet gear, thus the tip cylinder 41 of the first-side gear 4 is used as the supporting surface of the first-side planet gear, being supported on the inner wall of the first bore 61, and the tip cylinder 41 of the first-side planet gear 4 and the inner wall of the first bore 61 machined in planet carrier 6 compose a friction pair components; similarly, the tip cylinder 51 of the second-side planet gear 5 is used as the supporting surface of planet gear 5, being supported on the inner wall of the second bore 62, and the tip cylinder of the second-side planet gear 5 and the inner wall of the second bore 62 machined in planet carrier 6 compose a friction pair components. Therefore, during the working process of the differential according to present invention, the planet carrier 6 of the differential transforms the input torque into the normal pressure on one side of the tip cylinder 41 of the first-side planet gear 4 and the normal pressure on one side of the tip cylinder 51 of the second-side planet 5, the normal pressure applied on the first-side planet gear 4 and second-side planet gear 5 are separately balanced by a pair of tangent and radial forces generated in the process of the planet gear engaging with either the first-side annular gear 2 or the second-side annular gear 3 and the engagement between planet gears. Once the slip occurs or the tendency of slip appears, this normal pressure will generate a friction torque proportional to the input moment, which will directly lead to a bias in the distribution of the tangent force the first-side planet gear 4 and second-side planet gear applied individually to the first-side annular gear 2 and second-side annular gear 3, making the component with a lower angular speed get larger torque to increase the input torque applied to the driving wheel or axle with higher adhesive force, and the component with higher angular speed get less torque to limit the slip of the driving wheel or the axle which is connected to it.
Similar to available differentials, as illustrated in figures 1 and 4, the differential according to present invention also comprises a pair of end covers 13 and 14 fixed to both ends of the differential case 1.
For present invention as illustrated in figures 1 and 4, the third bore 11 and forth bore 12 are machined in differential case 1 or planet carrier 6, the said first-side annular gear 2 situated in the third bore 11 with sliding fit, and the said second-side annular gear 3 situated in the forth bore 12 with sliding fit. Therefore, either the first-side annular gear 2 or second-side annular gear 3 engages with only one planet gear, for each internal gear pair composed of an annular gear and a planet gear is asymmetric in structure, the tangential and radial force applied on the annular gear is also asymmetric, cannot be balanced by other tangential and radial force generated in engagement process, the excircle of the annular gear will be squeezed closely onto the inner wall of the bore machined in either the differential case 1 or planet carrier 6, therefore the excircle 21 of the first-side annular gear 2 and the inner wall of the third bore 11 compose a pair of friction components, similarly, the excircle 31 of the second-side annular gear 3 and the inner wall of the forth bore 12 also compose a pair of friction components.
For present invention, since the first-side annular gear 2 engages with only one first-side planet gear 4, and the second-side annular gear 3 engages also with only one second-side planet gear 5, the tangential and radial force applied on the annular gear is asymmetric, cannot be balanced by other tangential and radial force generated in engagement, thus the two forces must be balanced by the normal pressure of the inner wall of the bore 11 and 12 in differential case or planet carrier applied on the annular gears. Once the slip occurs or the tendency of slip appears, this normal pressure will generate a pair of friction moment proportional to the input torque, which will make the component with lower angular speed get part of the torque directly from the input end of the differential to increase the driving torque applied to the driving wheel or axle with higher adhesive force, and reduce the torque applied to the component with higher angular speed to get a further limitation to the slip of the driving wheel or axle connected to it.
For present invention as illustrated in figures 1 and 4, no rolling bearings are mounted on the said first-side annular gear 2 and second-side annular gear 3, the first-side annular gear 2 and second-side annular gear are individually situated in the third bore 11 and forth bore 12 with sliding fit. Since there are no rolling bearings arranged in the differential according to present invention, the components are arranged close to each other, being characterized by compact structure and higher load capacity. For present invention, as illustrated in figures 1 and 4, the said first-side annular gear 2, second-side annular gear 2, first-side planet gear 4 and second-side planet gear can be helical gears with the same helix angle or spur gears without helix angle, the helix angles at individual reference circles are the same or all equal to zero. If helical gears are adopted, among the gears the first-side planet gear 4 and second-side planet gear 5 have an inverse hand of helix, while the first-side planet gear 4 and first-side annular gear 2 have the same hand of helix, and the second-side planet gear 5 and second-side annular gear 3 have the same hand of helix. If helical gears are adopted, the axial thrusts generated on the first-side planet gear 4 when it engages with the first-side annular gear 2 and second-side planet gear 5 can be basically balanced with each other, and the axial thrusts generated on the second-side planet gear 5 when it engages with the second-side annular gear and first-side planet gear 4 can also be basically balanced with each other, but the axial thrusts applied on the first-side annular gear 2 and second-side annular gear 3 will generate normal pressure proportional to the input torque between the first-side annular gear 2, second-side annular gear 3 and the end cover 13, 14 or the ends 63, 64 of the planet carrier. Once the slip occurs or the tendency of slip appears, this normal pressure will generate a pair of friction moment proportional to the input torque, which will make the component with lower angular speed get part of the torque directly from the input end of the differential to increase the driving torque applied to the driving wheel or axle with higher adhesive force, and reduce the torque applied to the component with higher angular speed to get a further limitation to the slip of the driving wheel or axle connected to it. For present invention, since a number of slide faces are involved in the structure, even if spur gears are adopted, enough slip-limit ability can still be obtained, and straight annular gears are easier to manufacture. Adopting helical gear can make the differential work more smoothly.
For present invention, the friction pairs composed of the tip cylinder 41 of the first-side planet gear 4 and the first bore 61 machined in planet carrier 6, the tip cylinder 51 of the second-side planet gear and the second bore 62 machined in planet carrier 6, the excircles of the first-side and second-side annular gears and the third and forth bores 11 and 12, and the end planes of the first-side and second-side annular gears 2 and 3 and the end covers 13 and 14 or the ends 63 and 64 of the planet carrier 6 under the effect of input torque can generate enough friction moment to limit the slip of a certain driving wheel connected to some axle. Since the normal pressure between friction pair components is proportional to the input torque, its slip-limit ability is proportional to the input torque.
For present invention as illustrated in figures 1 to 7, the differential case 1 and planet carrier 6 can be integrated into one component. As another choice in embodiment, the differential case and planet carrier can be separately manufactured and fixed together. For present invention as illustrated in figures 1 and 4, in order to reduce the contact stress between tooth surfaces, the axial contact width between the first-side planet gear 4 and second-side planet gear 5 is larger then the axial contact width either between the first-side planet gear 4 and first-side annular gear 2 or the contact width between the second-side planet gear 5 and second-side annular gear 3. For present invention, the choice of the number of teeth in the gears in epicyclic train should meet required distribution of output torque between output sides, that means the ratio between the number of teeth in the first-side annular gear and second-side annular gear is close to required torque distribution ratio, while the number of teeth and modification coefficient in planet gears only need to meet the mounting condition, i.e. the axes of both annular gears coincide with each other, and no interference occurs.
In practice, for present invention, to increase supporting area and improve the resistance to wear of the tip cylinder 41 of the first-side planet gear 4 and tip cylinder 51 of second-side planet gear 5 those are used as the journals of sliding bearings, the tooth width of planet gears are increased in design process, and smaller pressure angle between 14.5 and 17.5 degrees or smaller addendum coefficient between 0.8 and 0.9 can be adopted.
As a preferred embodiment as illustrated in figures 1 to 3, the limited-sip differential according to present invention is to be used in a final reduction gear to distribute power to left and right driving wheels. For the embodiment, the first and second sides are corresponding respectively to the right and left sides of driving direction of the vehicle. The input power (which is not illustrated in figure 1) applies to differential case 1, and required theoretical torque distribution is 1 :1, therefore the number of teeth in the first-side annular gear 2 (the right-side annular gear) and second-side annular gears 3 (the left-side annular gear) is the same and equal to 28, while the number of teeth in the first-side planet gear 4 (the right-side planet gear) and second-side planet gear (the left-side planet gear) is the same and equal to 14 and all annular and planet gears are spur gears. A 20 degree pressure and addendum coefficient of 0.9 are adopted to get a larger tip width. As long as the torque distribution ratio between annular gears is within 1 :3.2 to 3.2:1, no slip in the differential will occur, possessing a rather high ability in slip limitation, meanwhile no drag will occur when the vehicle turns.
As another preferred embodiment as illustrated in figures 4 to 7, the differential is situated in a branch box, the input power is applied to the differential case, the first side annular gear 2 is connected to the front axle through a front driving shaft, and the second side annular gear 3 is connected to the rear axle through a rear driving shaft. For this embodiment, the first and second sides are respectively corresponding to the front and rear sides of the vehicle. The required theoretical torque ratio is 1:1.5, thus the number of teeth in the first-side annular gear 2 (the front-side annular gear) is chosen to be 22, and the number of teeth in the second-side annular gear 3 (the rear-side annular gear) is 33, the number of teeth in the first-side planet gear 4 (the front-side planet gear) is 13, and the number of teeth in the second-side planet gear 5 (the rear-side planet gear) is 14, the theoretical torque distribution ratio coincides with the requirement. For this embodiment, the said first-side planet gear 4 can extend form the first-side annular gear 2 to second-side annular gear 3 along axial direction, and contact the second-side planet gear 5 in whole tooth width of the second-side planet gear 5, so that the contact width "between two external planet gears is increased, and the contact strength is reduced. Some angular modification is used in planet gears to meet required centerline distance. In order to be easier to manufacture, a normal pressure angle of 20 degrees is used for planet and annular gears. The addendum coefficient is chosen to be 0.8, so that a wider tip width and larger supporting area can be obtained, and the wear and tear in the tip cylinders 41 and 51 and the first and second bores 61 and 62 can be decreased. All the gears used in the differential are spur gears, and the range of output torque ratio between the first-side annular gear 2 and second-side annular gear 3 is between 1 :4.8 and 2.13 : 1 , a rather high ability in slip limitation is obtained, meanwhile on power recycling will occur.
The parameters according to present embodiments are used to demonstrate the invention, not used as a limitation to the invention.

Claims

1. A kind of limited-slip differential with an asymmetric structure, comprises of a differential case and a planet carrier located within the differential case, wherein the differential also comprises of: a first-side annular gear and a second-side annular gear, individually located individually in the first and second ends of the differential case, as two output sides of the differential; a first-side planet gear and a second-side planet gear, individually located in the bores of the planet carrier, engages with each other, meanwhile the first-side planet gear also engages and only engages with the first-side annular gear, and the second-side planet gear also engages and only engages with the second-side annular gear; a first bore machined in the planet carrier, and the said first-side planet gear located in the bore with sliding fit, with its tip cylinder being utilized as the supporting surface, being supported on the inner wall of the first bore, and the tip cylinder of the first-side planet gear and the inner wall of the first bore compose a pair of friction components; a second bore machined in the planet carrier, and the said second-side planet gear located in the bore with a sliding fit, with its tip cylinder being utilized as the supporting surface, being supported on the inner wall of the second bore, and the tip cylinder of the second-side planet gear and the inner wall of the second bore compose a pair of fiictional components.
2. The limited-slip differential with an asymmetric structure according to Claim 1, wherein the third and forth bores are also machined in either the differential case or the planet carrier, the said first-side annular gear located in the third bore with sliding fit, composing a pair of friction components, and the second-side annular gear located in the forth bore with sliding fit, composing a pair of friction components.
3. The limited-slip differential with an asymmetric structure according to Claim 1, wherein two end covers are individually fixed to each end of the differential case.
4. The limited-slip differential with an asymmetric structure according to Claim 1, wherein the said differential case and planet carrier are separate.
5. The limited-slip differential with an asymmetric structure according to Claim I3 wherein the contact width between the said first-side planet gear and second-side planet gear is larger than either the contact width between the first-side planet gear and first-side annular gear or the contact width between the second-side planet gear and second-side annular gear.
6. The limited-slip differential with an asymmetric structure according to Claim 1, wherein the said first-side planet gear and second-side planet gear adopt a smaller pressure angle between 14.5 to 17.5 degrees or a smaller addendum coefficient between 0.8 and 0.9.
7. The limited-slip differential with an asymmetric structure according to Claim 1, wherein the said first-side annular gear and second-side annular gear adopt a smaller pressure angle between 14.5 to 17.5 degrees or a smaller addendum coefficient between 0.8 and 0.9. _
8. The limited-slip differential with an asymmetric structure according to Claim I5 wherein the said differential is used in a final reduction gear of a driving axle, the said first-side annular gear and second-side annular gear have the same number of teeth.
9. The limited-slip differential with an asymmetric structure according to Claim 1, wherein the said differential is used in a branch box, the input power is applied to the differential case, the first-side annular gear is connected to the front axle through a front driving shaft, and the second-side annular gear is connected to the rear axle through a rear driving shaft, the number of teeth in the first side annular gear is less than that in the second side annular gear.
10. The limited-slip differential with an asymmetric structure according to Claim 1, wherein on the premise that no interference occurs, the first-side planet gear can extend form the first-side annular gear to second-side annular gear along axial direction, and contact the second-side planet gear in whole tooth width of the second-side planet gear.
PCT/CN2007/001353 2007-02-16 2007-04-24 A kind of limited-slip differential with an asymmetric structure WO2008101371A1 (en)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013167316A1 (en) * 2012-05-07 2013-11-14 Schaeffler Technologies AG & Co. KG Differential gear, in particular in the form of an axle differential gear
CN112883485A (en) * 2021-01-22 2021-06-01 燕山大学 Non-circular face gear limited slip differential and escaping operation method

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101994812B (en) * 2009-08-11 2015-08-05 洪涛 Differential gear with limited differential ratio

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5030185A (en) * 1987-05-08 1991-07-09 Osamu Kawamura Limited slip differential
US5616096A (en) * 1994-08-18 1997-04-01 Viscodrive Japan Ltd. Differential gear unit
CN2366309Y (en) * 1999-04-09 2000-03-01 周殿玺 Fully automatic skid proof arrangement
US20030092527A1 (en) * 2001-11-09 2003-05-15 Caringella Anthony R. Limited slip differential
CN2823684Y (en) * 2005-04-08 2006-10-04 株洲齿轮有限责任公司 Parallel shaft planetary wheel type screw gear sliding limiting differential gear

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5030185A (en) * 1987-05-08 1991-07-09 Osamu Kawamura Limited slip differential
US5616096A (en) * 1994-08-18 1997-04-01 Viscodrive Japan Ltd. Differential gear unit
CN2366309Y (en) * 1999-04-09 2000-03-01 周殿玺 Fully automatic skid proof arrangement
US20030092527A1 (en) * 2001-11-09 2003-05-15 Caringella Anthony R. Limited slip differential
CN2823684Y (en) * 2005-04-08 2006-10-04 株洲齿轮有限责任公司 Parallel shaft planetary wheel type screw gear sliding limiting differential gear

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013167316A1 (en) * 2012-05-07 2013-11-14 Schaeffler Technologies AG & Co. KG Differential gear, in particular in the form of an axle differential gear
CN112883485A (en) * 2021-01-22 2021-06-01 燕山大学 Non-circular face gear limited slip differential and escaping operation method
CN112883485B (en) * 2021-01-22 2022-04-01 燕山大学 Non-circular face gear limited slip differential and escaping operation method

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