• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The present invention provides a differential device capable of always obtaining a stable differential limiting force even at low speed rotation. That is, in the present invention, a plurality of rollers are provided between the raceway surface that is integrally rotated with the input side rotating body and the raceway surface that is integrally rotated with each output side rotating body, and the transmission shaft of each roller is rotated with respect to the rotational axis of each raceway surface. The angle of inclination formed is smaller than 20 °, and the angle of inclination formed by the transmission shaft of each roller 6 with respect to the plane including the rotation axis of each raceway surface is greater than 25 ° and smaller than 90 °, so that the distance between each roller and each raceway surface is reduced. A stable frictional force can be generated at all times, and a differential limiting force can be obtained without causing stick slip even in low-speed rotation.
    公开号:KR20000056956A
    申请号:KR1019990021689
    申请日:1999-06-11
    公开日:2000-09-15
    发明作者:겐지 미무라
    申请人:겐지 미무라；
    IPC主号:
    专利说明:

    Differential Device {DIFFERENTIAL GEAR}
    The present invention relates to a differential device that permits a difference in the rotation of the left and right or front and rear drive wheels of an automobile.
    BACKGROUND ART A conventional vehicle differential device includes a pinion gear interposed between a pair of bevel gears connected to an output shaft, and in case of a differential, the pinion gear is rotated to allow rotation of each output shaft. In addition, as a differential device having a differential limiting function, a multiple plate clutch is disposed on the back side of the bevel gear, and the differential plate is limited by generating a friction force by pressing the plate plate clutch with the thrust force of the bevel gear.
    However, in a mechanism that transmits power by using sliding friction in a semi-connected state, such as the multi-plate clutch, a so-called stick slip occurs when the clutch plates intermittently cause stop friction and movement friction in low-speed rotation, and thus the differential limiting force is unstable. There was a problem. In addition, there was a problem that noise or vibration occurs by the stick slim.
    The present invention has been made in view of the above problems, and an object thereof is to provide a differential device capable of always obtaining a stable differential limiting force even at low speed rotation.
    1 is a side cross-sectional view of a differential device showing a first embodiment of the present invention;
    2 is a cross-sectional view taken along the line I-I of FIG.
    3 is a side cross-sectional view of a main portion of a differential device;
    4 is an exploded view of the roller and the cage,
    5 a and b are schematic views showing the inclination angle of the roller,
    6 a and b are explanatory diagrams of the operation of the differential device;
    7 and 8 are views showing the relationship between the inclination angle of the roller and the friction torque;
    Fig. 9 is a cross sectional view taken along the line II-II in Fig. 4 showing the case where each raceway surface and the outer peripheral surface of the roller are formed in a straight line shape;
    10 is a cross-sectional view taken along the line II-II in FIG. 4 showing an example in which each raceway surface is formed in a curved shape;
    11 is a cross-sectional view taken along the line II-II of FIG. 4 showing an example in which the outer circumferential surface of the roller is formed in a curved shape;
    12 is an exploded view of a roller and a cage showing another example of the arrangement of the rollers;
    13A and 13B are schematic views showing the inclination angles of the rollers,
    14 shows the relationship between the inclination angle of the roller and the friction torque;
    Fig. 15 is a side sectional view of a differential device showing the second embodiment of the present invention;
    16 is a cross-sectional view taken along the line III-III of FIG. 15;
    17 is a partial cross-sectional view taken along the line IV-IV of FIG. 15.
    In order to achieve the above object, the present invention provides an input side rotating body that rotates an axial circumference by a driving force input from the outside, a pair of output side rotating bodies coaxially formed with the input side rotating body, and an output side rotating body. A differential device having a differential transmission mechanism for transmitting a rotational force of an input side rotating body to each output side rotating body while allowing a whole rotational difference, and integrally rotating with the raceway surface and the output side rotating body integrally with the input side rotating body. A plurality of rollers which are disposed between the raceways and each output side rotating body makes a rotation difference with each other, and which rotates while contacting the raceways, and which rollers keep each roller freely spaced apart in the circumferential direction of each raceway. The holding body is provided, and the transmission shaft of each roller makes the angle smaller than 20 degrees with respect to the rotation shaft of the input side and the output side rotating body. The inclination is inclined so as to form an angle larger than 25 ° and smaller than 90 ° with respect to a plane including the rotation shafts of the input and output rotors. As a result, when the output rotors rotate with each other, the rollers rotate while contacting each raceway surface. At that time, the rollers are constrained by the roller retainer to rotate in the direction inclined with respect to the rotational trajectory of each raceway, while the rollers move along the rotational trajectory of each raceway, so that friction force is generated between each roller and each raceway. do. In this case, the inclination angle formed by the transmission shaft of each roller with respect to the rotation axis of the rotating body is smaller than 20 °, and the inclination angle formed by the transmission shaft of each roller with respect to the plane including the rotation axis of the rotation body is larger than 25 ° and smaller than 90 °. As a result, a stable frictional force always occurs.
    In the second invention, in the differential device of the first invention, the transmission shaft of each of the rollers is inclined to form an angle larger than 5 ° with respect to the rotation shafts of the input and output rotors, and includes the rotation shafts of the input and output rotors. Inclined in the same direction so as to form a predetermined angle with respect to the plane. As a result, when the output rotors rotate with each other, the rollers rotate while contacting each raceway surface. At that time, the rollers are constrained by the roller retainer to rotate in the direction inclined with respect to the rotational trajectory of each raceway, while the rollers move along the rotational trajectory of each raceway, so that friction force is generated between each roller and each raceway. do. In this case, a stable frictional force is always generated by increasing the inclination angle of the rotating shaft of each roller with respect to the rotating shaft of the rotating body to be greater than 5 ° and inclining in the same direction with respect to the plane including the rotating shaft.
    In the third invention, in the differential device of the first invention, the transmission shaft of each of the rollers is inclined to form an angle larger than 3 ° with respect to the rotation shafts of the input and output rotors, and includes the rotation shafts of the input and output rotors. The predetermined number is inclined in the opposite direction so as to form a predetermined angle with respect to the plane. As a result, when the output rotors rotate with each other, the rollers rotate while contacting each raceway surface. At that time, the rollers are constrained by the roller retainer to rotate in the direction inclined with respect to the rotational trajectory of each raceway, while the rollers move along the rotational trajectory of each raceway, so that friction force is generated between each roller and each raceway. do. At that time, if the input and output rotors are rotated, some of the rollers inclined in the same direction are intended to rotate in one direction of the axial direction of the rotor, while the rollers inclined in the other direction attempt to rotate in the axial direction of the other side of the rotor. It is possible to arbitrarily set the magnitude of the frictional force in each rotational direction of the rotating body by the number of rollers inclined in the opposite direction. In this case, a stable frictional force is always generated by increasing the inclination angle of the rolling shaft of each roller with respect to the rotating shaft of the rotating body to be greater than 3 °.
    In the fourth invention, in the differential device of the third invention, rollers which are inclined in opposite directions with respect to a plane including the rotating shafts of the input and output side rotors are alternately arranged in the circumferential direction of the input and output rotors. Doing. Thus, in addition to the effect of the third invention, the same frictional force is generated even when the roller is rotated in any direction.
    In the fifth invention, in the differential device of the first, second, third or fourth invention, the respective raceway surfaces are formed to be convex with respect to the outer circumferential surface of the roller in the cross section including the transmission shaft of the roller. Doing. Thus, in addition to the action of the first, second, third or fourth invention, it is possible to reduce the contact pressure at both ends in the axial direction of the roller.
    In the sixth invention, in the differential device of the first, second, third or fourth invention, the outer circumferential surface of each roller is convex with respect to each raceway surface in the cross section including the transmission shaft of the roller. Forming. It is thereby possible to reduce the contact pressure at both ends of the axial direction of the roller in addition to the action of the first, second, third or fourth invention.
    Therefore, according to the differential device of the first aspect of the invention, frictional force can be generated even at low rotation speed without causing stick slip, so that the frictional force can always obtain a stable differential limiting force, and furthermore, it is possible to reliably prevent the occurrence of noise and vibration. Can be. Moreover, since the magnitude | size of a friction force can be changed by setting the inclination-angle of each roller to arbitrary magnitude | size, it is possible to obtain the differential limiting force according to the objective.
    In addition, according to the differential device of the second invention, in addition to the effect of the first invention, a more effective and stable frictional force can be generated. In this case, since different frictional forces can be generated depending on the rolling direction of the roller, it is very advantageous for the purpose of such an operation.
    In addition, according to the differential device of the third aspect of the invention, in addition to the effects of the first aspect of the invention, an effective and stable frictional force can always be generated as in the second aspect of the invention. In this case, since the magnitude | size of the frictional force in each rolling direction of a roller can be set arbitrarily, it can be applied broadly according to a use.
    In addition, according to the differential device of the fourth aspect of the invention, in addition to the effects of the third aspect of the invention, the same frictional force can be generated even when the rollers are driven in any direction, which is very advantageous in the case of such an operation.
    In addition, according to the differential apparatuses of the fifth and sixth inventions, in addition to the effects of the first, second, third or fourth inventions, the contact pressure on both ends of the roller in the axial direction with respect to each raceway surface can be reduced. Uneven wear of the roller can be reduced, and durability can be improved.
    (Example)
    1 to 8 show a first embodiment of the present invention.
    The differential device comprises a gear case cover (2) that closes one end of the gear case (1) and the gear case (1), a pair of bevel gears (3) disposed coaxially opposite to each other, and each bevel gear. A plurality of pinion gears 4 disposed between the three, a pair of pressure rings 5 which rotate integrally with the gear case 1, each pressure ring 5 and each bevel gear 3; A plurality of rollers 6 arranged between the plurality of rollers, a cage 7 for holding each roller 6 freely at intervals, and each pressure ring 5 for pressing the bevel gears 3, respectively. It consists of a pair of cone springs (8), the gear case (1), the gear case cover (2) and each pressure ring (5) constitute an input side rotor, each bevel gear 3 constitutes an output side rotor have.
    The gear case 1 has a cylindrical shape with one end open, and a bearing 1a for supporting one bevel gear 3 is provided on the other end side. The flange 1b is provided in the circumference | surroundings of the gear case 1, and the hole 1c for bolting in is provided in the flange 1b. In addition, a plurality of grooves 1d extending in the axial direction are provided on the inner surface of the gear case 1 at intervals in the circumferential direction.
    The gear case cover 2 is formed in a disk shape, and a bearing 2a for supporting the other bevel gear 3 is provided at the center thereof. A flange 2b is formed around the gear case cover 2, and a plurality of holes 2c for bolting in the flange 2b are provided. That is, the gear case cover 2 is assembled to the gear case 1 by bolts (not shown) which fasten the flanges 1b and 2b to each other.
    Each bevel gear 3 opposes a tooth surface side, and each has the connection part 3a with the drive shaft of the wheel side not shown. On the back side of each bevel gear 3, a raceway surface 3b is formed opposite to the pressure ring 5, and the raceway surface 3b forms a tapered shape around the axis of rotation, and at the same time as shown in FIG. In the parallel cross section, it is formed to form a concave curve.
    Each pinion gear 4 is rotatably installed on the pinion shaft 4a supported by the gear case 1, and is engaged with each bevel gear 3, respectively.
    Each of the pressure rings 5 is formed in an annular shape around the rotating shaft, and a plurality of projections 5a are fitted to the groove 1d of the gear case 1 on the outer circumferential surface thereof. That is, each pressure ring 5 is freely supported by the gear case 1 in the axial direction, respectively. In addition, a raceway surface 5b is formed on the inner circumferential surface of each pressure ring 5 so as to face the raceway surface 3b of the bevel gear 3, and the raceway surface 5b has a tapered shape around the rotation axis. At the same time, as shown in Fig. 3, the cross section parallel to the rotation axis is formed to have a convex curve.
    Each roller 6 has the cylindrical shape which the outer peripheral surface extends equally in the axial direction, and is arrange | positioned at equal intervals in the circumferential direction of each track surface 3b, 5b.
    The cage 7 is formed in an annular shape around the rotating shaft, and forms a tapered shape along the raceways 3b and 5b, and at the same time, the thickness thereof is smaller than the outer diameter of each roller 6. The cage 7 is provided with a plurality of holes 7a for freely accommodating each roller 6, and the holes 7a are arranged at equal intervals in the circumferential direction. In this case, each hole 7a is formed so that the transmission shaft of each roller 6 may incline in the same direction, respectively, as shown in FIG. Moreover, as shown in FIG. 5A, the transmission shaft 6a of each roller 6 forms the inclination angle (alpha) 1 with respect to the rotation shaft 1b of the gear case 1, respectively, and as shown in FIG. 5B, the rotation shaft 1b The angle of inclination beta 1 is achieved with respect to a plane including In this case, the inclination angle α1 of each roller 6 is set larger than 5 degrees and smaller than 20 degrees, and the inclination angle β1 is set larger than 25 degrees and smaller than 90 degrees. Incidentally, the inclination angle β1 is an angle viewed from the direction orthogonal to the transmission shaft 6a of the roller 6.
    Each cone spring 8 is arranged on the back side of each bevel gear 3, and one cone spring 8 is located between the inner surface of the gear case 1 and the pressure ring 5 of the other. The cone spring 8 is installed in the axial direction between the inner surface of the gear case cover 2 and the pressure ring 5 on the other side, respectively.
    In the differential device configured as described above, a ring gear (not shown) connected to the engine side is provided on the flange 1b of the gear case 1, and the gear case 1 is rotated by the driving force from the engine. have. In this case, if there is a rotational difference in each drive shaft, such as during the turning of the curve, each pinion gear 4 between the bevel gears 3 rotates to achieve a differential of each drive shaft. In addition, when the driving force is applied to the gear case 1, each bevel gear 3 and each pinion gear 4 are axial thrust force to each bevel gear 3 by the inclination of the tooth surface which meshes with each other, That is, a force to move in the direction away from the pinion gear 4 is generated. As a result, when a rotation difference occurs in each drive shaft, each roller 6 is pressed against the raceway surface 3b of each bevel gear 3 and the raceway surface 5b of each pressure ring 5, and is electrically driven. The differential limiting force is generated by the frictional force between (6) and the raceways 3b and 5b. In this case, the preload by each cone spring 8 is given to each roller 6 and each raceway surface 3b, 5b.
    That is, as shown in FIG. 6A, when the raceway surface 3b of the bevel gear 3 rotates in one direction while applying the thrust force F in the axial direction (hereinafter referred to as forward rotation), each roller 6 The cage to be driven in one of the axial directions of the rotating shaft, that is, the direction inclined by the angle β1 with respect to the rotational trajectory (the direction in which the respective raceway surfaces 3b and 5b decrease in diameter) as indicated by the broken line arrow in the drawing. Thrust force between each roller 6 and each raceway surface 3b, 5b because it is regulated by (7) and is driven along the trajectory of rotation of each raceway surface 3b, 5b as shown by the solid arrow in the figure. A frictional force proportional to (F) occurs. As shown in Fig. 6B, when the raceway surface 3b rotates in a different direction (hereinafter referred to as reverse rotation), each roller 6 is on the other side in the axial direction of the rotation axis, that is, as indicated by the broken line arrow in the drawing. It is regulated by the cage 7 to rotate in the direction inclined by the angle β1 with respect to the rotation trajectory (the direction in which the diameters of the respective raceway surfaces 3b and 5b become larger), and as shown by the solid arrows in the drawing, the respective raceways Since the rollers are driven along the rotational tracks of the surfaces 3b and 5b, frictional force proportional to the thrust force F is generated between the rollers 6 and the raceway surfaces 3b and 5b. At that time, since each roller 6 generates sliding friction while rolling, no static friction is generated and stable resistance is always obtained by motion friction, and even if static friction occurs at an initial stage, The motor moves to movement friction at the moment. In the stationary rotation of the raceway surface 3b, the rollers 6 are driven in a direction in which the diameters of the raceway surfaces 3b and 5b become smaller. In the reverse rotation, the rollers 6 rotate each raceway surface 3b and 5b. Even when the thrust force F is the same by rolling in the direction in which the diameter increases, the magnitude of the frictional force generated by the rotational direction of the raceway surface 3b is different, and the frictional force in the forward rotation is greater than the frictional force in the reverse rotation. Grows
    In the above embodiment, when the rollers 6 on one bevel gear 3 side are driven in a direction in which the diameters of the track surfaces 3b and 5b become smaller (or larger), the other bevel gear ( By arranging the rollers 6 on the side of each bevel gear 3 so that each roller 6 on the 3) side rolls in the direction of increasing (or decreasing) the diameter of each raceway surface 3b, 5b, The same differential limiting force can be generated in any rotational direction of the bevel gear 3.
    However, the applicant has experimented and analyzed theoretically the relationship between the inclination angles α1 and β1 of each roller and the friction torque P in the range of 3 ° to 40 ° for the inclination angle α1 and 5 ° to 85 ° for the inclination angle β1. It was confirmed by.
    That is, as shown in FIG. 7, when the inclination angle (alpha) 1 of each roller 6 in the forward rotation of the raceway surface 3b is 5 degrees or less, the friction torque P rapidly increases as the inclination angle (beta) 1 becomes small. It becomes large, and each roller 6 and each track surface 3b, 5b become a state which is easy to lock mutually. If the inclination angle α1 is larger than 5 °, the sudden fluctuation of the friction torque P does not appear.However, if the inclination angle α1 is 20 ° or more, the friction is not less than the practically effective value regardless of the magnitude of the inclination angle β1. Torque P cannot be obtained. On the other hand, when the inclination angle β1 of each roller 6 is larger than 25 °, except for the case where the inclination angle α1 is 5 ° or less, the friction torque P does not show a sudden change, but the inclination angle β1 is 25 When the temperature is lower than or equal to, the friction torque P is greatly reduced, and the friction torque P higher than the practically effective value cannot be obtained. As shown in Fig. 8, when the raceway surface 3b is in reverse rotation, the friction torque P is equally decreased when the inclination angle 1 is smaller in any case, but the inclination angle ( When α1) is 20 ° or more, the friction torque P more than a practically effective value cannot be obtained regardless of the magnitude of the inclination angle β1. In addition, even when the inclination angle α1 is smaller than 20 °, the friction torque P larger than the practically effective value cannot be obtained when the inclination angle β1 is 25 ° or less. Moreover, although the case where the inclination angle (beta) 1 was larger than 85 degrees was not confirmed actually, it is estimated from the said experimental data that the friction torque P with the inclination angle (beta) 1 to 90 degrees becomes substantially the same as the case of 85 degrees.
    Thus, according to the differential apparatus of this embodiment, the track surface 5b of each pressure ring 5 which rotates integrally with the gear case 1, and the track | orbit of each bevel gear 3 which rotates integrally with each drive shaft A plurality of rollers 6 are provided between the surfaces 3b, and the angle α1 formed by the transmission shaft of each roller 6 with respect to the rotation axes of the raceway surfaces 3b and 5b is greater than 5 ° and greater than 20 °. Each roller 6 is made smaller by less than 90 degrees by making the angle β1 formed by the transmission shaft of each roller 6 with respect to the plane containing the rotation shaft of each track surface 3b, 5b at the same time smaller than it. Since stable friction force can always be generated between and the raceway surfaces 3b and 5b, it is possible to obtain a differential limiting force without causing stick slip even at low speed rotation. In this case, since the magnitude of the frictional force can be changed by setting the inclination angle of each roller 6 to an arbitrary size, it is also possible to obtain a differential limiting force in accordance with the purpose.
    Moreover, in the structure of the said embodiment, as shown in FIG. 9, each track surface 3b, 5b in the arrow direction sectional drawing of the II-II line of FIG. 4, ie, the cross section including the transmission shaft 6a of the roller 6, is shown. Is brought into contact with the outer circumferential surface of the roller 6 uniformly in the axial direction, the contact pressure of both ends of the axial direction of the roller 6 becomes larger than the center side. Therefore, as shown in FIG. 10, when each raceway surface 3b, 5b in the cross section containing the transmission shaft of the roller 6 is made into the curved shape which forms convex shape with respect to the outer peripheral surface of the roller 6, respectively. The contact pressure at both ends of the axial direction of the roller 6 can be reduced. Therefore, by forming the curved shape of each raceway surface 3b, 5b so that the contact pressure in the axial direction of the roller 6 may be equal, the wear of the roller 6 can be reduced. 11, even when each track surface 3b, 5b is formed in a linear shape in the cross section including the transmission shaft of the roller 6, the outer circumferential surface of the roller 6 is each track surface 3b, The effect equivalent to the above can be acquired by making it into the curve shape which makes a convex shape with respect to 5b).
    12 to 14 show another arrangement example of the rollers, FIG. 12 is an exploded view of the roller and the cage, FIG. 13 is a schematic view showing the inclination angle of the roller, and FIG. 14 is a view showing the relationship between the inclination angle of the roller and the friction torque. to be.
    That is, each roller 6 shown in the said figure is inclined in the opposite direction alternately by the same number with respect to the plane containing the rotating shaft of the rotating body 1. As shown in FIG. As shown in FIG. 13A, the transmission shaft 6a of each roller 6 forms a predetermined inclination angle α2 with respect to the rotation shaft 1b of the gear case 1, and simultaneously shows the rotation shaft 1b as shown in FIG. 13B. Each makes a predetermined angle of inclination β2 with respect to the plane including. In this case, the inclination angle α2 of each roller 6 is set larger than 3 ° and smaller than 20 °, and the inclination angle β2 is set larger than 25 ° and smaller than 90 °. Incidentally, the inclination angle β2 is an angle viewed from the direction orthogonal to the transmission shaft 6a of the roller 6.
    As described above, frictional force proportional to the thrust force F in the axial direction is generated between the rollers 6 and the track surfaces 3b and 5b as in the above-described embodiment. In this case, since the rollers 6 are alternately inclined in the opposite direction by the same number with respect to the plane including the rotating shafts of the respective raceway surfaces 3b and 5b, the same frictional force is generated in any rotational direction of the raceway surface 3b. .
    In the present embodiment, the Applicant regards the relationship between the inclination angles α2 and β2 of each roller and the friction torque P in the range of 3 ° to 40 ° for the inclination angle α2 and 5 ° to 85 ° for the inclination angle β2. It was confirmed by experiment and theoretical analysis.
    That is, as shown in Fig. 14, even when the inclination angle α2 of each roller is smaller, the friction torque P is equally reduced when the inclination angle β2 is decreased, but when the inclination angle α2 is 20 ° or more, the inclination angle Regardless of the magnitude of (β2), the friction torque P beyond the practically effective value cannot be obtained. Further, even when the inclination angle α2 is smaller than 20 °, the friction torque P larger than the practically effective value cannot be obtained when the inclination angle β2 is 25 ° or less. In addition, when the inclination angle β2 is larger than 85 degrees, it was not actually confirmed, but according to the experimental data, it is assumed that the friction torque P up to the inclination angle β2 is 90 degrees, which is almost the same as that of 85 degrees.
    15 to 17 show a second embodiment of the present invention. In addition, the same code | symbol is attached | subjected to the structural part equivalent to 1st Embodiment, and the detailed description is abbreviate | omitted.
    In other words, the differential device of the present embodiment includes a gear case cover 2 that closes one end of the gear case 10 and the gear case 10, a pair of bevels 11 disposed to face each other coaxially, A plurality of pinion gears 12 disposed between each bevel gear 11, a pair of first pressure rings 13 which rotate integrally with the gear case 10, and integrally with each bevel gear 11. A plurality of rollers 6 disposed between the pair of rotating second pressure rings 14 and the first and second pressure rings 13 and 14, respectively, and each roller 6 is freely spaced apart from each other. The cage 7 to be retained, the pair of cone springs 8 which press each of the first pressure rings 13 toward the respective second pressure rings 14, and each of the second pressure rings 14, respectively 1 consists of a pair of third pressure rings 15 pressed towards the pressure ring 13, the gear case 10, the gear case cover 2 and each of the first and third pressure rings 13 and 15 are input side Construct a rotating body, Bevel gears 11 and each of the second pressure ring 14 constitute a full output times.
    The gear case 10 has a cylindrical shape with one end open, and a bearing 100a for supporting one bevel gear 11 is provided on the other end side. The flange 10b is provided around the gear case 10, and the flange 10b is provided with a number of holes 10c for bolting. In addition, a plurality of grooves 10d extending in the axial direction are provided on the inner surface of the gear case 10 at intervals in the circumferential direction. In addition, illustration of the flange 10b is abbreviate | omitted in FIG.
    Each bevel gear 11 opposes a tooth surface side, and each has the connection part 11a with the drive shaft of the wheel side not shown. On the back side of each bevel gear 11, a plurality of grooves 1lb extending in the axial direction are provided at intervals in the circumferential direction.
    Each pinion gear 12 is rotatably provided on the pinion shaft 12a, and meshes with each bevel gear 11, respectively.
    Each of the first pressure rings 13 is formed in an annular shape around the rotating shaft, and a plurality of protrusions 13a are fitted on the outer circumferential surface of each of the grooves 10d of the gear case 10. That is, each first pressure ring 13 is freely supported in the axial direction by the gear case 10, respectively. Moreover, the raceway surface 13b which opposes the 2nd pressure ring 14 is formed in the inner peripheral surface of each 1st pressure ring 13.
    Each of the second pressure rings 14 is formed in an annular shape around the rotational shaft, and a plurality of protrusions 14a are fitted on the inner circumferential surface thereof to fit the grooves 11b of the bevel gears 11, respectively. . In other words, each second pressure ring 14 is freely supported by each bevel gear 11 in the axial direction. Moreover, the raceway surface 14b which opposes the raceway surface 13b of the 1st pressure ring 13 is formed in the inner peripheral surface of each 2nd pressure ring 14. As shown in FIG. Moreover, each raceway surface 13b, 14b in this embodiment is formed like 1st embodiment.
    Each third pressure ring 15 is formed to cover each bevel gear 11 and each pinion gear 12 at both ends in the axial direction, and the outer circumferential surface of each third pressure ring 15 in each groove 10d of the gear case 10. A plurality of projections 15a to be fitted are provided at intervals in the circumferential direction. That is, each of the third pressure rings 15 is freely supported by the gear case 10 in the axial direction, respectively, and at one end of each of the second pressure rings 14 in the axial direction (the track surface 14b is the track surface ( 13b) in the direction of approaching the sheet. In addition, a plurality of V-shaped grooves 15b are provided on the opposite surface of each of the third pressure rings 15 at intervals in the circumferential direction. As shown in FIG. 17, the pinion shaft 12a is provided in each of the grooves 15b. It is accepted.
    In the differential device configured as described above, a ring gear (not shown) connected to the engine side is provided on the flange 10b of the gear case 10, and the gear case 10 is rotated by the driving force from the engine. . In this case, when a rotation difference occurs in the drive shafts (not shown) of both drive wheels, such as during the turning of the curve, the respective pinion gears 12 between the bevel gears 11 rotate, and the differential of each drive shaft is achieved. When the driving force is applied to the gear case 10, the V-shaped grooves 15b of the third pressure rings 15 are pressed against the pinion shaft 12a, and as shown in Fig. 17, the grooves 15b Thrust force F of the axial direction is produced in each 3rd pressure ring 15 by the inclined surface. As a result, when a rotation difference occurs in each drive shaft, the rollers 6 rotate while being pressed against and contact the raceways 13b and 14b of the first and second pressure rings 13 and 14, respectively. The differential limiting force is generated by the frictional force of the respective raceway surfaces 13b and 14b. In addition, the inclination angle of each roller 6 and the principle of generating the friction force are the same as in the first embodiment.
    As described above, according to the differential device of the present embodiment, the frictional force is generated by the rolling of the rollers 6 as in the first embodiment, so that a stable differential limiting force can always be obtained, and at the same time, Thrust force can be reliably generated by pressing, so an effective differential limiting force can always be obtained.
    权利要求:
    Claims (6)
    [1" claim-type="Currently amended] The rotational force of the input side rotating body is allowed while allowing the rotational difference between the input side rotating body which rotates around the axial center by the driving force input from the outside, a pair of output side rotating bodies coaxially formed with the input side rotating body, and each output side rotating body. In a differential device having a differential transmission mechanism for transmitting to each output side rotor,
    A plurality of rollers disposed between the raceway surface that is integrally rotated with the input side rotor and the raceway surface that is integrally rotated with the output side rotor; ,
    A roller holder for freely holding each roller at intervals in the circumferential direction of each raceway surface,
    Incline the transmission shaft of each roller to form an angle smaller than 20 ° with respect to the rotation axis of the input and output rotors, and at an angle greater than 25 ° and smaller than 90 ° with respect to the plane including the rotation axes of the input and output rotors. Differential device, characterized in that inclined.
    [2" claim-type="Currently amended] The method of claim 1,
    The rollers are inclined to form an angle greater than 5 ° with respect to the rotary shafts of the input and output rotors, and are inclined in the same direction to form a predetermined angle with respect to a plane including the rotary shafts of the input and output rotors. Differential device, characterized in that.
    [3" claim-type="Currently amended] The method of claim 1,
    The rotating shafts of the rollers are inclined so as to form an angle greater than 3 ° with respect to the rotation shafts of the input and output rotating bodies, and at the same time in a predetermined number of directions so as to form a predetermined angle with respect to the plane including the rotating shafts of the input and output rotating bodies. Differential device, characterized in that inclined with.
    [4" claim-type="Currently amended] The method of claim 3,
    And rollers inclined in opposite directions with respect to a plane including rotation shafts of the input and output rotors, alternately arranged in the circumferential direction of the input and output rotors.
    [5" claim-type="Currently amended] The method according to any one of claims 1 to 4,
    And each said raceway surface is formed in convex shape with respect to the outer peripheral surface of a roller in the cross section including the transmission shaft of a roller.
    [6" claim-type="Currently amended] The method according to any one of claims 1 to 4,
    And the outer circumferential surface of each roller is formed so as to form a convex shape with respect to each raceway surface in the cross section including the transmission shaft of the roller.
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    同族专利:
    公开号 | 公开日
    JP2000230629A|2000-08-22|
    ID24787A|2000-08-16|
    CN1263220A|2000-08-16|
    KR100395891B1|2003-08-25|
    CA2273780A1|2000-08-12|
    TW454071B|2001-09-11|
    AU3395199A|2000-08-17|
    US6056664A|2000-05-02|
    JP3444807B2|2003-09-08|
    EP1028274A1|2000-08-16|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    法律状态:
    1999-02-12|Priority to JP11-34189
    1999-02-12|Priority to JP3418999A
    1999-06-11|Application filed by 겐지 미무라
    2000-09-15|Publication of KR20000056956A
    2003-08-25|Application granted
    2003-08-25|Publication of KR100395891B1
    优先权:
    申请号 | 申请日 | 专利标题
    JP11-34189|1999-02-12|
    JP3418999A|JP3444807B2|1999-02-12|1999-02-12|Differential device|
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