WO2007071115A1 - Differentiel interponts a glissement limite a couple divise - Google Patents

Differentiel interponts a glissement limite a couple divise Download PDF

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Publication number
WO2007071115A1
WO2007071115A1 PCT/CN2005/002299 CN2005002299W WO2007071115A1 WO 2007071115 A1 WO2007071115 A1 WO 2007071115A1 CN 2005002299 W CN2005002299 W CN 2005002299W WO 2007071115 A1 WO2007071115 A1 WO 2007071115A1
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WO
WIPO (PCT)
Prior art keywords
pinions
sun gear
inter
torque limited
planetary
Prior art date
Application number
PCT/CN2005/002299
Other languages
English (en)
Inventor
Xiaochun Wang
Hong Jiang
Original Assignee
Xiaochun Wang
Hong Jiang
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Xiaochun Wang, Hong Jiang filed Critical Xiaochun Wang
Priority to PCT/CN2005/002299 priority Critical patent/WO2007071115A1/fr
Publication of WO2007071115A1 publication Critical patent/WO2007071115A1/fr

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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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/34—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles
    • B60K17/344—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear
    • B60K17/346—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear the transfer gear being a differential gear
    • B60K17/3462—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear the transfer gear being a differential gear with means for changing distribution of torque between front and rear wheels
    • B60K17/3465—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear the transfer gear being a differential gear with means for changing distribution of torque between front and rear wheels self-actuated means, e.g. differential locked automatically by difference of speed
    • 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 generally to a kind of inter-axle differential for the vehicles with multiple driving axles, and particularly to inter-axle split-torque limited-slip differentials.
  • an arrangement of multiple driving axles is widely used in many SUV, cross-country trucks and engineering wheel vehicles.
  • inter-axle differentials are widely adopted to distribute the torque and power among driving axles. Since the load is usually unequally distributed among the axles, to make the full use of the adhesive force on each driving wheel to get the maximum driving force, it is necessary that the differential can distribute the torque unequally to driving axles.
  • inter-axle differential based on planetary gear set which is composed of sun gear, planetary pinions and ring gears is currently in wide usage.
  • This kind of differential utilizes the difference in the number of teeth in sun gear and ring gear to get the different torque distribution between the both output ends of the differential.
  • a vehicle equipped with common planetary inter-axle differential may lose its driving force when it drive on bad road surface and the adhesive force on one of the driving axle suddenly drops.
  • some off-road vehicles use toothed clutches instead of inter-axle differentials, and the driver needs to choose whether or not the driving power is applied to front axle.
  • slip limit mechanisms such as preload multiple friction plates or friction plates with adhesive liquid are added to inter-axle differentials to limit its slip.
  • slip limit mechanism are not only complicated in structure, heavier and larger in volume, but also exist some limitations in their performance.
  • the preload friction mechanism cannot automatically adjust the preload in accordance to input torque or the load on the output ends, so a certain preload may be not enough to a heavily loaded truck, but too large to an empty one and lead to power circulation.
  • 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.
  • 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 object of the present invention is to provide a type of inter-axle differential with the character that its slip limit ability is proportional to the input torque of the differential, and without considering the inner friction, the torque ratio between the both output ends can nearly meet the required torque ratio, being compact in structure and easy to maintain.
  • the technical scheme of the present invention is a limited-slip ' inter-axle differential at least involves:
  • a differential case A sun gear, being located in the differential case;
  • Plural planetary pinions surrounding the sun gear and engaging with the sun gear;
  • a ring gear being coaxal to the sun gear and engaging with the planetary gears;
  • a planet carrier fixed in the differential case, transmitting the input torque to the planetary pinions and keeping the pinions in position;
  • End covers fixed to both ends of the differential case.
  • the characteristic is that a set of bores corresponding to each planetary pinion are made in the planet carrier, the said planetary pinions are settled in the bores in the planet carrier by snug fit, and utilize the top lands of the pinions as the bearing surface which is supported in the bores, composing plural sliding bearings with the inner wall of the bores.
  • the said sun gear and ring gear are settled in floating mode, their radial positions are automatically determined in the engagement process.
  • the said sun gear, the planetary pinions and ring gear are helical gears with large helix angle. On their reference circle, all gears have the same helix angle.
  • the sun gear has a different hand of helix to the pinions, while the pinions have the same hand of helix to the ring gear.
  • the ratio between the frictional torque generated by the pinion top lands and the input torque of the differential is mainly depended on the ratio of the outer diameter of the pinions to the size of the epicyclic train, while the latter is determined by the required split ratio between the output torques of the differential.
  • the main approach to adjust the slip limit ability of the differential is realized by adjusting the helix angle of the gear pair.
  • the said helix angle of the gear pairs is between 30 to 75 degrees.
  • the axial position of the sun gear, ring gear and planetary pinions individually have some end backlash.
  • Each member can make a small axial float.
  • the axial backlash of the said planetary pinions is larger than those of the sun gear and ring gear, to ensure all the axial thrusts generated on the sun gear and ring gear are applied to the end plane of the end covers or the ends of the planet carrier so as to increase the friction torque.
  • the friction pairs composed of the top lands of the pinion and the bores in the planet carrier, the end planes of the sun gear and ring gears and the end planes of the differential end covers or the planet carrier will generate enough frictional torque under the effect of the input torque of the differential to limit the spinning of the driving axles.
  • the said planet carrier may integrate into the differential case or be independent to the case.
  • the selection of the number of teeth in the gears of the epicyclic train should meet the requirement of torque distribution, i.e. the ratio between the number of teeth of the sun gear and the number of teeth of the ring gear is nearly the required ratio between the both output torques, meanwhile the requirement of uniform distribution of the pinions in the planetary carrier had better be satisfied.
  • the number of teeth of all the members in the epicyclic train must be selected in such a way that the requirement of uniform distribution of the pinions in the planetary carrier along the circumference of the sun gear is satisfied.
  • the mode of the distribution of the pinions in the planet carrier is depended on whether or not the number in teeth of the sun gear and ring gear can meet the condition for uniform distribution of the pinions. If the condition for uniform distribution of pinions can be satisfied, the pinions are uniformly distributed around the sun gear; otherwise in case the uniform distribution of the pinions cannot be satisfied, the pinions can be arranged in groups, and the groups are uniformly distributed around the sun gear.
  • the better scheme is that the number of pinions is between 2 and 8.
  • the sun gear and the ring gear are separated in axial direction in design process so as to increase the length of the pinions and the area of the top lands to reduce the pressure in unit area and improve their abrasion resistance.
  • smaller normal pressure angle or short-addendum profile can be adopted.
  • the small pressure angle from 14.5 to 17.5 degrees or smaller addendum coefficient between 0.8 and 0.9 can be adopted.
  • a combined washer can be inserted between the sun gear shoulder and the differential end cover, which may practically be composed of a flat washer and a toothed washer by means of cohesion, spot welding or riveting.
  • a flat washer can be settled between the ends of the said pinions and the inner end of the end cover.
  • the planet carrier of the differential transforms the input torque into the normal pressure on one side of the top lands of the planetary pinions when the differential works, and the normal pressure acted on each pinion is balanced by a pair of tangent forces generated in the process of the pinion engaging with both the sun gear and ring gear.
  • this normal pressure will generate a frictional torque proportional to the input torque, which will directly lead to a bias in the distribution of the tangent force applied individually to the sun gear and ring gear, making the component with a lower angular speed get larger torque to increase the input torque of the axle with higher adhesive force, and the component with higher angular speed get less torque to limit the slip of the driving wheels of the axle which is connected to it.
  • the normal pressures will generate a pair of frictional torque proportional to the input torque of the pinion.
  • One of the frictional torques will directly transmit some torque from the input torque to the member with lower angular speed to increase the torque transmitted to the axle with higher adhesive force, while the other frictional torque will reduce the torque transmitted to the member with higher angular speed to limit the slip of the driving wheels of the axle which is connected to it. Since there are no rolling bearings in the differential, the planetary pinions can be arranged closer to each other, being characterized by compact structure and higher load capacity.
  • FIG. 1 is a schematic section view of the differential according to present invention
  • FIG. 2 is a schematic view of the structure of the planet carrier
  • FIG 3 is the section view A-A of FIG 2;
  • FIG. 4 and 5 is a schematic view of the structure of the combined washer to the sun gear
  • FIG. 6 and 7 are the schematic view of the structure of the planetary pinion.
  • the inter-axle limited-slip differential involves at least a differential case 1 and a sun gear 2 settled in the differential case, plural planetary pinions 3 which engage with the sun gear 2 and are settled around the sun gear 2, and a ring gear 4 which is settled coaxial with the sun gear and engages with the planetary pinions, the planet carrier 5 which locates in the differential case 1 , transmits the input torque to planetary pinions 3 and keeps their positions, and the end covers 11 and 12 fixed to both sides of the differential case 1, these components compose an epicyclic train.
  • the planet carrier has a series of bores 51 in the circumference of the sun gear corresponding to the planetary pinions, the said planetary pinions are settled in the bores in the planet carrier by snug fit.
  • the said pinions have neither journals nor rolling gearings fixed on them, but utilize their top lands 31 to fit the bores 51 made in the planet carrier to compose plural sliding bearings to position and support the planetary pinions.
  • the top lands 31 of the planetary gears 3 are used as the supporting surfaces of the planetary gears 3 which are supported by the wall of the bores 51, and the top lands 31 of the planetary gears 3 fit in the wall of the bores 51 to compose plural friction pairs.
  • the planet carrier 5 transforms the input torque into the normal pressure on one side of the top lands 31 of the planetary pinions 3, and the normal pressure acted on each pinion 3 is balanced by a pair of tangent forces generated in the process of the pinion 3 engaging with both the sun gear 2 and ring gear 4.
  • this normal pressure will generate a frictional torque proportional to the input torque, which will directly lead to a bias in the distribution of the tangent force from the planetary pinions 3 applied individually to the sun gear 2 and ring gear 4, making the component with a lower angular speed get larger torque to increase the input torque of the axle with higher adhesive force, and the component with higher angular speed get less torque to limit the slip of the driving wheels of the axle which is connected to it.
  • the said sun gears 2 and ring gears 4 have not mounted rolling bearings, the sun gear 2 and ring gear 4 are settled in floating mode, their radial positions are automatically determined in the engagement process. Therefore, since there are no rolling bearings in the differential, the planetary pinions can be arranged closer to each other, being characterized by compact structure and higher load capacity.
  • the said sun gear 2, planetary pinions 3 and ring gear 4 can be helical gears with large helix angle. On their reference circle, all gears have the same helix angle.
  • the sun gear 2 has a different hand of helix to the pinions 3, while the pinions 3 have the same hand of helix to the ring gear 4.
  • the axial position of the sun gear, ring gear and planetary pinions are not fixed but have some end backlash. Each member can make a small axial float.
  • the normal pressures will generate a pair of frictional torque proportional to the input torque of the pinion.
  • One of the frictional torques will directly transmit some torque from the input torque to the member with lower angular speed to increase the torque transmitted to the axle with higher adhesive force, while the other frictional torque will reduce the torque transmitted to the member with higher angular speed to limit the slip of the driving wheels of the axle which is connected to it.
  • the ratio between the frictional torque generated by the top lands 31 of the planetary pinions 3 and the input torque of the differential is mainly depended on the ratio of the outer diameter of the pinions to the size of the epicyclic train, while the latter is determined by the required split ratio between the output torques of the differential.
  • the main approach to adjust the slip limit ability of the differential is realized by adjusting the helix angle of the gear pair.
  • the said helix angle of the gear pairs according to present invention can be selected between 30 to 75 degrees.
  • the axial backlash of the said planetary pinions 3 is larger than those of the sun gear 2 and ring gear 4, to ensure all the axial thrusts generated on the sun gear 2 and ring gear 4 are applied to the end plane of the end covers 11, 12 of the differential case 1 or the ends 52 and 53 of the planet carrier 5 so as to increase the frictional torque.
  • the friction pairs composed of the top lands 31 of the pinions 3 and the wall of the bores 51 in the planet carrier 5, the end planes of the sun gear 2 and side gear 4 and the end planes of the differential end covers 11 and 12 or the planet carrier ends 52 and 53 will generate enough frictional torque under the effect of the input torque of the differential to limit the spinning of the driving wheel of some axle. Since the normal pressure acting on each friction pair is proportional to the input torque, the slip limit ability of the differential is proportional to the load applied on the differential.
  • the said planet carrier may integrate into the differential case or be independent to the case.
  • the contact area between the planetary pinions 3 and the sun gear 2 and the contact area between the pinions 3 and the ring gear 4 are separate in axial direction to increase the area of the top lands of the pinions 3, so as to reduce the pressure in unit area and improve the abrasion resistance of the pinion top lands 31 and the wall of the bores 51 in the planet carrier 5.
  • the selection of the number of teeth in the gears of the epicyclic train should meet the requirement of torque distribution, i.e. the ratio between the number of teeth in the sun gear 2 and the number of teeth in the ring gear 4 is nearly the required ratio between the both output torques, meanwhile the requirement of uniform distribution of the pinions 3 in the planetary earner 5 had better be satisfied.
  • the number of the pinions 3 is a prime
  • the number of teeth in all the members in the epicyclic train must meet the requirement of uniform distribution of the pinions 3 in the planetary carrier 5 along the circumference of the sun gear.
  • the mode of the distribution of the pinions 3 in the planet carrier 5 is depended on whether or not the number of teeth in the sun gear 2 and ring gear 4 can meet the condition for uniform distribution of the pinions 3. If the condition for uniform distribution of pinions 3 can be satisfied, the pinions 3 are uniformly distributed around the sun gear 2, otherwise the pinions 3 can be arranged in groups, and the groups are uniformly distributed around the sun gear 2.
  • the better scheme is that the number of pinions is between 2 and 8.
  • a combined washer 6 is settled between the shoulder of the sun gear 2 and the differential end cover 11, which may practically be composed of a flat washer and a toothed washer by means of cohesion, spot welding or riveting.
  • a flat washer 7 is settled between the ends of the said pinions 3 and the inner end of the end cover 11.
  • the sun gear and the ring gear are separated in axial direction in design process to increase the length of pinions, and smaller normal pressure angle or short-addendum gears can be adopted.
  • a small pressure angle from 14.5 to 17.5 degrees or smaller addendum coefficient between 0.8 and 0.9 can be adopted.
  • the differential of this invention is settled in transfer case, the input power is applied to the differential case.
  • the output from the sun gear is transmitted to front axle by front drive shaft, and the output from the ring gear is transmitted to rear axle by rear drive shaft.
  • the required output torque ratio is 1 :2.69.
  • the number of teeth in the sun gear is chosen to be 14, the number of teeth in the pinions is 12, and the number of teeth in the ring gear is 38.
  • the theoretical torque ratio is 1:2.71, being very close to the requirement.
  • the number of pinions 3 is 4, can meet the requirement that the pinions are uniformly distributed around the sun gear.
  • the normal pressure angle of the sun gear, planetary pinion and ring gear is chosen to be the standard value of 20 degrees.
  • Short-addendum gear profile with the addendum coefficient being 0.8 is adopted to increase the top land width and supporting area of the pinions so that the wear and tear in the pinion top land 31 and the bore 51 can be slowed down.
  • the helix angle of the gear pairs is chosen to be 45 degrees, and the range of possible output torque ratio between the sun gear 2 and ring gear 4 is between 1 :1.632 and 1 :5.284. Thus a differential of reasonable slip-limitation ability is achieved while the power circulation is avoided.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)

Abstract

La présente invention concerne un type de différentiel interponts à glissement limité à couple divisé comportant un train épicycloïdal qui est constitué d'un boîtier de différentiel (1), d'un planétaire (2), d'engrenages planétaires (3), d'une couronne (4). Des alésages (51) sont formés dans le porte-satellites (5) et les engrenages planétaires (3) sont installés dans les alésages du porte-satellites en un ajustement serré. Les surfaces de tête (31) des engrenages planétaires (3) et la paroi des alésages (51) réalisées dans le porte-satellites (5) constituent une pluralité de paires de frottement. Le différentiel selon l'invention se caractérise en ce que sa capacité de limitation de glissement est proportionnelle au couple d'entrée, par sa structure compacte et son entretien facile.
PCT/CN2005/002299 2005-12-23 2005-12-23 Differentiel interponts a glissement limite a couple divise WO2007071115A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/CN2005/002299 WO2007071115A1 (fr) 2005-12-23 2005-12-23 Differentiel interponts a glissement limite a couple divise

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/CN2005/002299 WO2007071115A1 (fr) 2005-12-23 2005-12-23 Differentiel interponts a glissement limite a couple divise

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WO2007071115A1 true WO2007071115A1 (fr) 2007-06-28

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PCT/CN2005/002299 WO2007071115A1 (fr) 2005-12-23 2005-12-23 Differentiel interponts a glissement limite a couple divise

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2123943A3 (fr) * 2008-05-23 2011-05-04 Jtekt Corporation Porte-satellites, mécanisme d'engrenage de type planétaire et différentiel de véhicule doté de ceux-ci

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5194054A (en) * 1990-04-25 1993-03-16 Viscodrive Gmbh Differential drive
US6080076A (en) * 1997-11-17 2000-06-27 Gkn Viscodrive Gmbh Mechanical locking differential
JP2003056672A (ja) * 2001-08-10 2003-02-26 Bosch Automotive Systems Corp 差動歯車装置
CN2623964Y (zh) * 2003-06-12 2004-07-07 中国重型汽车集团有限公司 新型轴间差速器
US20050148424A1 (en) * 2004-01-07 2005-07-07 Toyoda Koki Kabushiki Kaisha Differential limiting device

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5194054A (en) * 1990-04-25 1993-03-16 Viscodrive Gmbh Differential drive
US6080076A (en) * 1997-11-17 2000-06-27 Gkn Viscodrive Gmbh Mechanical locking differential
JP2003056672A (ja) * 2001-08-10 2003-02-26 Bosch Automotive Systems Corp 差動歯車装置
CN2623964Y (zh) * 2003-06-12 2004-07-07 中国重型汽车集团有限公司 新型轴间差速器
US20050148424A1 (en) * 2004-01-07 2005-07-07 Toyoda Koki Kabushiki Kaisha Differential limiting device

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2123943A3 (fr) * 2008-05-23 2011-05-04 Jtekt Corporation Porte-satellites, mécanisme d'engrenage de type planétaire et différentiel de véhicule doté de ceux-ci
US8182387B2 (en) 2008-05-23 2012-05-22 Jtekt Corporation Planetary carrier, planetary gear mechanism, and vehicle differential provided with the same

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