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WO2013001617A1 - Dispositif de mécanisme de différentiel pour véhicule - Google Patents

Dispositif de mécanisme de différentiel pour véhicule Download PDF

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Publication number
WO2013001617A1
WO2013001617A1 PCT/JP2011/064845 JP2011064845W WO2013001617A1 WO 2013001617 A1 WO2013001617 A1 WO 2013001617A1 JP 2011064845 W JP2011064845 W JP 2011064845W WO 2013001617 A1 WO2013001617 A1 WO 2013001617A1
Authority
WO
WIPO (PCT)
Prior art keywords
pair
differential
disc spring
side gears
differential case
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/JP2011/064845
Other languages
English (en)
Japanese (ja)
Inventor
旭洋 槙野
吉村　孝広
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Toyota Motor Corp
Original Assignee
Toyota Motor Corp
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 Toyota Motor Corp filed Critical Toyota Motor Corp
Priority to PCT/JP2011/064845 priority Critical patent/WO2013001617A1/fr
Publication of WO2013001617A1 publication Critical patent/WO2013001617A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/08—Differential gearings with gears having orbital motion comprising bevel 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
    • F16H48/38—Constructional details
    • F16H2048/387—Shields or washers

Definitions

  • the present invention relates to a vehicle differential gear device for distributing power to a pair of left and right drive wheels of a vehicle, and more particularly to a technique for preventing an axle fitted in a side gear so as not to rotate relative to a side gear.
  • an annular leaf spring member is provided between a rear surface of the side gear and a receiving surface that receives the rear surface of the side gear of the differential case.
  • a receiving surface that receives the rear surface of the side gear of the differential case.
  • the differential limiting force can be obtained with a simple configuration, and when the transmission torque is relatively low, backlash at the meshing portion between the side gear and the pinion is reduced, and the generation of rattling noise is suppressed. Since the deformation of the annular leaf spring member allows the side gear to escape in the direction of the rotation axis, there is an advantage that the side gear is prevented from being damaged when an impact is input.
  • the backlash between the side gear and the pinion is made zero by the annular leaf spring member inserted in a pressurized state.
  • the reciprocation of the side gear in the direction of the rotational axis corresponding to the backlash fluctuation amount is performed.
  • the axle that is spline-fitted to the fitting hole formed through the center of the side gear so as not to rotate relative to the rotation axis and to be relatively movable in the direction of the rotational axis increases the slip resistance as the transmission torque increases, Above a certain torque, it reciprocates with the side gear.
  • the present invention has been made against the background of the above circumstances, and the object of the present invention is to provide an annular leaf spring member in a preloaded state between the back surface of the side gear and the receiving surface of the differential case that receives the back surface of the side gear.
  • An object of the present invention is to provide a vehicle differential gear device that can suitably prevent the possibility that the axle will come off the side gear and the possibility that the snap ring will come off even if it is inserted.
  • the gist of the present invention is that: (1) a differential case that is rotationally driven around the first axis, and a second case that is orthogonal to the first axis in the differential case.
  • a driving force provided with a pinion rotatably supported around an axis, and a pair of side gears arranged in the differential case so as to be relatively rotatable around the first axis with the pinion interposed therebetween, and meshing with the pinion.
  • a differential gear device for a vehicle that distributes power input from a power source to the differential case to drive wheels via a pair of axles coupled to the pair of side gears, comprising: (2) a rear surface of the side gear and the differential case An annular leaf spring member is inserted in a pre-loaded state between the receiving surface of the side gear and the rear surface of the side gear. At least one pair of symmetrical sites is characterized in that it is one that has a different spring characteristic from each other.
  • the annular leaf spring member inserted in a preload state between the back surface of the side gear and the receiving surface of the differential case that receives the back surface of the side gear is at least one pair with respect to the center of the annular leaf spring member. Since the symmetrical parts of the side gears have different spring characteristics, the inertial force in the reciprocating motion of the side gear rotating while being urged by the annular leaf spring member is suppressed, or the snap ring and Since the impact with the side gear is alleviated, the possibility that the axle will come out of the side gear and the possibility that the snap ring will come off are suitably prevented.
  • the annular leaf spring member is formed by a conical shape between an inner circumference circle and an outer circumference circle having the same center position, and a notch is formed in a part of the outer circumference circle. It is.
  • the disc spring is symmetrical with respect to the center position by forming a notch in a part of the outer circumference of the disc spring, and one pair of symmetrical parts including the notch is different from each other.
  • the annular leaf spring member is a disc spring in which a conical shape is formed between an inner circumference circle and an outer circumference circle whose center positions are eccentric.
  • the disc springs are eccentric in the center positions of the inner and outer circumferential circles, and the radial positions of the central positions, for example, the parts that are symmetric with respect to the center of the inner circumferential circle are different from each other.
  • the pair of symmetrical portions that are symmetric with respect to the center position have different spring characteristics. For this reason, the inertial force in the reciprocating motion of the side gear rotating while being urged by the disc spring is suppressed, or the impact between the snap ring and the side gear is mitigated. The possibility of coming off and the possibility of the snap ring coming off are suitably prevented.
  • FIG. 3 is a cross-sectional view illustrating a configuration of a disc spring used in the vehicle differential gear device of FIG. 1, and is a cross-sectional view taken along line III-III in FIG.
  • FIG. 3 is a schematic diagram which shows the structure of the differential gear apparatus for vehicles for demonstrating the effect
  • FIG. 6 is a cross-sectional view illustrating the configuration of the disc spring of FIG. 5, and is a cross-sectional view taken along the line VI-VI of FIG. 5. It is a front view explaining the disk spring of the other Example of this invention.
  • FIG. 8 is a cross-sectional view illustrating the configuration of the disc spring of FIG. 7 and is a cross-sectional view taken along the line VIII-VIII of FIG. It is a front view explaining the conventional disc spring.
  • FIG. 10 is a cross-sectional view illustrating the configuration of the conventional disc spring of FIG. 9 and is a cross-sectional view taken along the line XX-X in FIG. It is a schematic diagram which shows the structure of the differential gear apparatus for vehicles for demonstrating the effect
  • FIG. 1 is a diagram for explaining a vehicle differential gear device (differential device) 10 to which the present invention is preferably applied, in which a rotational axis C1 of axles 24l and 24r and a pinion shaft (small gear shaft) orthogonal thereto. ) Is a cross-sectional view cut along a plane including 18 axis C2.
  • a vehicle differential gear device 10 includes a differential case 12 made of, for example, cast iron or powder alloy, which is rotatably supported around a shaft center C1 by a housing (not shown) via a pair of roller bearings.
  • Both ends of the differential case 12 are supported by a large-diameter ring gear 14 that is fixed to the outer peripheral portion of the differential case 12 by a fastener 13 such as a bolt and receives power from a drive source such as an engine or an electric motor, and the differential case 12.
  • a fastener 13 such as a bolt
  • a drive source such as an engine or an electric motor
  • the differential case 12 In a state where the pinion shaft 18 is fixed to the differential case 12 by the knock pin 16 in a posture in the direction of the axis C2 orthogonal to the rotational axis C1 of the differential case 12, and the differential is in a state of being opposed to each other across the pinion shaft 18.
  • the differential case 12 is connected to a pair of left and right drive wheels Wl and Wr such as a pair of left and right front wheels or a rear wheel of the vehicle through joints CP such as constant velocity universal joints, respectively.
  • 1 shows only a pair of left and right through holes 26l and 26r that rotatably support an axle 24r corresponding to the right wheel. Since the pair of side gears 20l and 20r and the pair of axles 24l and 24r fitted in such a manner that they cannot be rotated relative to each other have the same configuration, the configuration of the right side gear 20r and axle 24r is representative. This will be described below.
  • a fitting groove (spline groove) 28 is formed on the outer peripheral surface of the end portion of the axle 24r, and a fitting tooth (spline tooth) 30 is formed on the inner peripheral surface of the side gear 20r so as to engage with the fitting groove 28.
  • the axle 24r that is formed and inserted into the through hole 26r is fitted so that the fitting groove 28 and the fitting teeth 30 on the inner peripheral surface of the side gear 20r are engaged with each other, whereby the side gear It is configured such that it cannot rotate relative to the rotation axis C1 common to 20r and can move in the direction of the rotation axis C1, and can rotate integrally with its side gear 20r.
  • annular groove 32 for fitting the snap ring 34 is formed on the outer peripheral portion at the shaft end of the axle 24r, and the snap ring 34 fitted into the annular groove 32 is a pinion shaft of the side gear 20r.
  • the pair of side gears in a state where the pair of annular plate washers 36 and the pair of annular disc springs 38 pressurized in the direction of the rotation axis C1 are overlapped with each other.
  • 20l and 20r are biased in the direction toward the pinion gear 22.
  • a convex disk-shaped spherical washer 40 having a partial spherical shape and having a hole through which the pinion shaft 18 is passed in the center, with the pinion shaft 18 passing therethrough, the outer peripheral side end surfaces (back surfaces) of the pair of pinion gears 22 It is inserted between the inner wall surface of the differential case 12.
  • the plate washer 36 and the spherical washer 40 are made of a wear-resistant metal, for example, a lead-based or Sn-based bearing metal, or a metal obtained by adding spring properties to the alloy as required.
  • the disc spring 38 corresponds to the annular leaf spring member of the present invention.
  • the disc springs 38 are mutually centered positions which are positions of the rotation axis C1 in FIGS. Are formed in an annular shape having the same inner circumference circle 42 and outer circumference circle 44, and the space between the inner circumference circle 42 and the outer circumference circle 44 is formed in a conical shape, and a part of the outer circumference circle 44 is equally spaced in the circumferential direction. Thus, three linear notches 46 are formed.
  • the disc spring 38 is configured by punching and press molding from a spring plate material.
  • the disc spring 38 configured in this manner has a notch 46, so that one of the pair of symmetrical portions that are symmetrical with respect to the center position of the inner circumferential circle 42 and the outer circumferential circle 44 is notched.
  • FIG. 2 a pair of symmetric parts including the symmetric part 48 and the symmetric part 50 will be described.
  • the radial dimension of the symmetric part 48 is larger than the radial dimension of the symmetric part 50 whose radial dimension is reduced by the notch 46.
  • the elastic coefficient (stress / displacement) is relatively smaller than that of the symmetrical portion 50.
  • FIG. 4 is a schematic diagram for explaining the retaining prevention action of the vehicle differential gear device 10 of the present embodiment provided with the disc spring 38, and the dimensional ratios and the like of the respective parts are not necessarily drawn as in the actual case. .
  • the disc spring 38 is one of the symmetrical portions 48, 50 in a symmetrical position with respect to the center position of the inner circumferential circle (inner circumferential surface) 42 and the outer circumferential circle 44 (outer circumferential surface). Since the spring characteristics of the pair of symmetrical portions 48 and 50 including the notch 46 are different from each other, the biasing force received from the disc spring 38 is not equal to the rotational axis C1 in the side gears 20l and 20r.
  • the insertion is performed between the rear surfaces of the side gears 20l ⁇ and 20r and the receiving surface of the differential case 12 that receives the rear surfaces of the side gears 20l and 20r in a preload state.
  • the disc spring (ring leaf spring member) 38 is rotated while being urged by the disc spring 38 since at least one pair of symmetrical portions with respect to the center of the disc spring 38 have different spring characteristics.
  • the disc spring (ring annular leaf spring member) 38 has a conical shape between the inner circumferential circle 42 and the outer circumferential circle 44 having the same center position. Three notches 46 are formed in a part of the outer circumferential circle 44. For this reason, the disc spring 38 has a pair of symmetrical portions 48 and 50 which are symmetrical with respect to the center position and one of which includes the cutout, by forming a notch 46 in a part of the outer circumference circle 44.
  • the springs have different spring characteristics, the inertial force in the reciprocating motion of the side gears 20l20 and 20r rotating while being urged by the disc spring 38 in the direction of the rotation axis C1 is suppressed, or alternatively, the snap ring 34 and the side gears 20l20 and 20r. Therefore, the possibility that the axles 24l and 24r come out of the side gears 20l and 20r and the possibility that the snap ring 34 is detached from the axles 24l and 24r are suitably prevented.
  • FIGS. 9 and 10 are a front view and a cross-sectional view of a disc spring 138 used in a conventional differential gear device for a vehicle.
  • the disc spring 138 is formed by punching and press-molding from a spring plate material so that a conical shape is formed between the concentric inner and outer circumferential circles 42 and 44 having the rotation axis C1 as the center position.
  • the disc spring 138 has a pair of symmetrical portions that are symmetrical with respect to the center position thereof, the side gears 20l and 20r are separated from the disc spring 38 as shown in the schematic diagram of FIG.
  • the biasing force received is equal to the rotational axis C1 and reciprocates in the direction of the rotational axis C1 without tilting during the differential operation.
  • FIG. 5 is a front view for explaining the configuration of a disc spring 60 according to another embodiment of the present invention
  • FIG. 6 is a view showing a cross section taken along line VI-VI in FIG.
  • the disc spring 60 of the present embodiment is used in place of the disc spring 38 of the above-described embodiment, and is a concentric inner circumferential circle (an inner circumferential surface) 42 having the rotation axis C1 as the center position.
  • an outer circumferential circle (an outer circumferential surface) 44, and a conical shape is formed between the inner circumferential circle 42 and the outer circumferential circle 44, and a linear notch 46 is formed at one location of the outer circumferential circle 44.
  • a notch 46 is formed in a part of the outer circumference circle 44.
  • the disc spring (annular leaf spring member) 60 has a space between the inner circumference circle 42 and the outer circumference circle 44 having the same center position. Since the conical shape is formed and one notch 46 is formed in a part of the outer circumference circle 44, the disc spring 60 is formed by forming the notch 46 in a part of the outer circumference circle 44. A pair of symmetrical portions 48, 50 that are symmetrical with respect to position and one of which includes the notch have different spring characteristics.
  • FIG. 7 is a front view for explaining the configuration of a disc spring 70 according to another embodiment of the present invention
  • FIG. 8 is a view showing a section taken along line VIII-VIII in FIG.
  • the disc spring 70 of the present embodiment is used in place of the disc spring 38 of the above-described embodiment, and includes an inner circumferential circle (an inner circumferential surface) 72 centered on the rotation axis C1 and its inner circumference.
  • An outer circumferential circle (an outer circumferential surface) 74 having a center position C74 decentered from the center of the circle 72, and punching and press forming from the spring plate material so that a space between the inner circumferential circle 72 and the outer circumferential circle 74 has
  • the disc spring (the ring-shaped leaf spring member) 70 has a conical shape between the inner circumference circle 72 and the outer circumference circle 74 whose center positions are eccentric. Since the disc spring 70 is formed in a shape, the center position of the inner circumference circle 72 and the outer circumference circle 74 is eccentric, and the symmetrical portion 48 is symmetric with respect to the center position, for example, the center of the inner circumference circle 72. , 50 are formed so that the radial dimensions thereof are different from each other, so that the pair of symmetrical portions 48 and 50 that are symmetric with respect to the center position have mutually different spring characteristics.
  • the pair of pinion gears 22 is arranged between the side gear 20l and the side gear 20r, but an even number such as four may be arranged at equal intervals in the circumferential direction. An odd number such as three may be arranged at equal intervals in the circumferential direction.
  • the disc springs 38, 60, 70 of the above-described embodiment are plates that are inserted in a preload state between the back surfaces of the side gears 20l, 20r and the receiving surfaces of the differential case 12 that receive the back surfaces of the side gears 20l, 20r.
  • the plate washer 36 may not be provided, but, on the contrary, the plate washer 36 may sandwich the disc springs 38, 60, and 70, for example.
  • a plurality of sheets may be provided.
  • the direction of the rotation axis C1 of the disc springs 38, 60, 70 may be opposite to the direction shown in FIG.
  • the disc spring 38 shown in FIGS. 2 and 3 or the disc spring 60 shown in FIGS. 5 and 6 of the above-described embodiment is provided with a linear notch 46 in a part of the outer circumference circle 44 thereof.
  • the pair of symmetrical portions 48 and 50 which are symmetrical with respect to the center position and one of which includes the above-described notches, are configured to have different spring characteristics.
  • an arc-shaped notch may be formed in a part of the inner circumferential circle 42.
  • the conical spring is formed between the inner circumferential circle 42 and the outer circumferential circle 44 whose center positions are concentric. Therefore, the disc springs 38 and 60 are straight on a part of the outer circumferential circle 44.
  • a straight notch 46 is provided in a part of the outer circumferential circle 44, so that it is symmetrical with respect to the center position and one of the pairs includes the notch 46.
  • the portions 48 and 50 are configured to have different spring characteristics, but may be formed so that the inclination angles with respect to the rotation axis C1 are different from each other at the pair of symmetrical positions. Even in this case, the pair of symmetrical portions 48 and 50 that are symmetrical with respect to the center position and one of which includes the notch 46 has different spring characteristics.
  • the disc springs 38, 60, and 70 of the above-described embodiments are all formed in a conical shape so as to function as springs that urge the side gears 20l and 20r ⁇ toward the pinion gear 22 side.
  • the annular leaf spring member is configured to have mutually different spring characteristics at a pair of symmetrical positions that are symmetrical with respect to the center position. You may do it.
  • the snap ring 34 is fitted to the shaft ends of the axles 24l and 24r.
  • the snap ring 34 may not necessarily be provided.
  • Differential gear device for vehicle 12 Differential case 20l, 20r: Side gear 24l, 24r: Axle 38, 60, 70: Belleville spring (annular leaf spring member) 32: annular groove 34: snap ring 42, 72: inner circumferential circle 44, 74: outer circumferential circle 46: notch 48, 50: symmetrical part

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

Abstract

L'invention concerne un dispositif de mécanisme de différentiel pour un véhicule avec lequel il est possible d'empêcher de manière optimale un axe de se séparer d'un planétaire de différentiel et d'empêcher un anneau élastique de se détacher, même quand un élément de ressort Belleville annulaire est précontraint et interposé entre le planétaire de différentiel et le carter de différentiel. Avec une rondelle Belleville (38), la section entre une circonférence intérieure (42) et une circonférence extérieure (44) ayant la même position centrale est façonnée dans une forme conique et des encoches (46) sont constituées en trois endroits sur des parties de la circonférence extérieure (44), ainsi la paire qui comprend les zones symétriques (48, 50), qui sont symétriques par rapport à la position centrale et dont une comporte une encoche (46), a des caractéristiques de ressort qui diffèrent l'une de l'autre. Par conséquent, la force d'inertie du mouvement de va-et-vient dans la direction (C1) de rotation de planétaires (20l, 20r) de différentiel, qui sont rappelés et tournés par la rondelle Belleville (38) est supprimée et le choc entre l'anneau élastique (34) et les planétaires (20l, 20r) de différentiel est atténué; il est ainsi possible d'empêcher de manière optimale les axes (24l, 24r) de se séparer des planétaires (20l, 20r) de différentiel.
PCT/JP2011/064845 2011-06-28 2011-06-28 Dispositif de mécanisme de différentiel pour véhicule Ceased WO2013001617A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/JP2011/064845 WO2013001617A1 (fr) 2011-06-28 2011-06-28 Dispositif de mécanisme de différentiel pour véhicule

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2011/064845 WO2013001617A1 (fr) 2011-06-28 2011-06-28 Dispositif de mécanisme de différentiel pour véhicule

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WO2013001617A1 true WO2013001617A1 (fr) 2013-01-03

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109139876A (zh) * 2018-08-20 2019-01-04 杭州杰途传动部件有限公司 一种混动汽车差速器

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS498723B1 (fr) * 1967-06-02 1974-02-28
US20070287569A1 (en) * 2006-06-07 2007-12-13 Sayid Miah Resiliently loaded side gears in a differential mechanism
US20070289408A1 (en) * 2005-04-25 2007-12-20 Cradit Jeremy L Differential assembly with spring-biased side gears

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS498723B1 (fr) * 1967-06-02 1974-02-28
US20070289408A1 (en) * 2005-04-25 2007-12-20 Cradit Jeremy L Differential assembly with spring-biased side gears
US20070287569A1 (en) * 2006-06-07 2007-12-13 Sayid Miah Resiliently loaded side gears in a differential mechanism

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109139876A (zh) * 2018-08-20 2019-01-04 杭州杰途传动部件有限公司 一种混动汽车差速器
CN109139876B (zh) * 2018-08-20 2024-02-09 杭州杰途传动部件有限公司 一种混动汽车差速器

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