JP2005249212A - Hybrid differential gear device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To increase a torque bias ratio between a pair of output members. <P>SOLUTION: The casing 23 of a second differential gear mechanism 3 is formed of a carrier 9 and a sun gear 22 separated from each other so that the casing 23 can be halved in the axial direction. A carrier 19 is formed movable in the axial (L) direction to pressingly bring it forming a part of the casing 23 into contact with the housing 11 through a washer by the meshing of a pinion gear 26 with a side gear 27A. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a hybrid differential gear device having a first differential gear mechanism and a second differential gear mechanism built in the first differential gear mechanism.

  As a conventional differential gear device of this type, for example, there is one described in Patent Document 1 below. A hybrid differential gear device described in this publication includes a housing (input member) that is rotationally driven, at least a pair of planetary gears that are provided in the housing in parallel with an axis thereof and capable of rotating, and in the housing. A pair of side gears (output members) provided so as to be rotatable with the axis line aligned with the axis line of the housing. The pair of planetary gears mesh with each other and with the pair of side gears. The housing, the planetary gear and the pair of side gears constitute a first differential gear mechanism, and the rotational torque input to the housing is distributed to the pair of side gears via the planetary gear.

  A casing of the second differential gear mechanism is provided so as to rotate integrally with one of the pair of side gears. Inside the casing, there are provided a pinion gear composed of a bevel gear whose axis is orthogonal to the axis of the casing, and a pair of second side gears composed of a bevel gear whose axis is aligned with the axis of the casing. The pinion gear and the second side gear are rotatably supported by the casing and mesh with each other. Therefore, the rotational torque distributed to one side gear is further distributed to the pair of second side gears. The rotational torque distributed to the second side gear is transmitted to, for example, left and right front wheels or rear wheels. On the other hand, the rotational torque distributed to the other of the pair of side gears is transmitted to the rear differential when the hybrid differential gear unit is used as the center and front differential, and the hybrid differential gear unit is used as the center and rear differential. Is transmitted to the front differential. Then, it is transmitted from the rear differential or the front differential to the left and right rear wheels or front wheels.

JP-A-10-220556

  In a vehicle provided with the hybrid differential gear device having the above-described configuration, it may be desired that the torque transmitted to the front wheels and the rear wheels have different magnitudes. In such a case, it is necessary to increase the ratio of the rotational torque transmitted to the pair of side gears as output members, that is, the torque bias ratio. However, in the conventional hybrid differential gear device, only the side gear and the planetary gear of the first differential gear mechanism are considered in order to increase the torque bias ratio between the pair of side gears. The mechanism was not considered at all. For this reason, there is a problem that it is difficult to further increase the torque bias ratio.

The present invention has been made to solve the above problems, and is an input member that is rotationally driven, a pair of output members that are rotated by the input member via a planetary gear, and the input member and the pair of outputs. A first differential gear mechanism having a housing containing a member; a casing provided in the housing; a pinion gear provided rotatably in the casing; and an axis line aligned with the inside of the casing. In a hybrid differential gear device including a second differential gear mechanism having a pair of side gears that are rotatably provided and meshed with the pinion gear, the casing is divided into two in the axial direction of the side gears, and two Among the parts of the casing divided into two, one part supporting the pinion gear can be rotated to the housing And a portion that is non-rotatably connected to one of the pair of output members and supports one of the pair of side gears, among the portions of the casing, is generated by the meshing of the pinion gear and the side gear. The pair of side gears are movable in the axial direction so that they are pressed against the housing by the pressing force in the axial direction of the side gears, thereby generating a frictional resistance between the part and the housing when the part rotates. It is characterized by that.
In this case, the casing is divided into two parts that support the pinion gear and one side gear and a part that supports the other side gear, and the part that supports the pinion gear and one side gear moves in the axial direction of the side gear. It is preferable that a part of the housing is also used as a part for supporting the other side gear.
The first differential gear mechanism includes an internal gear, a carrier, and a sun gear whose axes are aligned with each other, and a planetary gear that is rotatably provided on the carrier and meshes with the internal gear and the sun gear. Any one of the internal gear, the carrier, and the sun gear is preferably used as the input member, and the remaining two are used as the output member.

  According to the present invention having the above-described configuration, the casing of the second differential gear mechanism is divided into two, so that frictional resistance is generated between the casing and the housing during differential rotation of the first differential gear mechanism. Then, a rotational torque having a magnitude corresponding thereto is transmitted from one of the two output members that rotates at a high speed to the other that rotates at a low speed. As a result, an effect that the torque bias ratio can be increased is obtained.

The best mode for carrying out the present invention will be described below with reference to FIGS.
1 and 2 show a first embodiment of the present invention. The hybrid differential gear device A of this embodiment has a first differential gear mechanism 1 and a second differential gear mechanism 2. First, the first differential gear mechanism 1 will be described. Reference numeral 11 denotes a housing that is driven to rotate about the axis L. The housing 11 includes a pair of halves 12 and 13 disposed on one end side and the other end side in the axis L direction. The pair of halves 12 and 13 face each other with the ring gear 14 therebetween, and are fixed to each other by tightening a bolt 15 that passes through the half body 13 and the ring gear 14 and is screwed to the half body 12. At the same time, a ring gear 14 is fixed to each of the halves 12 and 13. The ring gear 14 is rotationally driven by an engine (not shown), so that the housing 11 is rotationally driven about the axis L.

  Journal portions 12a and 13a having a cylindrical shape are formed at end portions of the half bodies 12 and 13 which are separated from each other, and bearings 16 and 17 are provided in the respective journal portions 12a and 13a. The housing 11 is rotatably supported by a differential case (not shown) via the bearings 16 and 17. An annular protrusion 12 b that protrudes toward the bearing 16 is formed on the side surface of the half body 12 that faces the bearing 16. The annular protrusion 12b has an outer diameter substantially equal to the outer diameter of the bearing 16, and an annular space 18 is defined by the side portion of the half body 12 extending from the annular protrusion 12b to the journal portion 12a and the bearing 16. Is formed. Lubricating oil accommodated in the differential case enters the annular space 18 through a gap between the inner ring 16 a and the outer ring 16 b of the bearing 16. The lubricating oil that has entered the space 18 is introduced into the housing 11 through the through-hole 12 c formed in the side surface of the half 12 facing the space 18. About the protrusion part 12b and the through-hole 12c, it is desirable to employ | adopt also in each embodiment mentioned later.

A carrier (output member) 19 is provided inside the housing 11 so as to be rotatable with its axis aligned with the axis L and movable in the direction of the axis L. The carrier 19 is formed with a pair of outer housing holes 19a and inner housing holes 19b. The outer housing hole 19a and the inner housing hole 19b are formed in at least one pair (four pairs in this embodiment). The plurality of pairs of outer and inner receiving holes 19 a and 19 b are arranged at equal intervals in the circumferential direction of the carrier 19. The outer accommodation hole 19 a is disposed on the outer peripheral side of the carrier 19, and the outer peripheral side portion is open to the outside from the outer peripheral surface of the carrier 19. On the other hand, the inner accommodation hole 19 b is disposed inside the outer accommodation hole 19 a, and the inner peripheral side portion is open to the outside from the inner peripheral surface of the carrier 19. Further, the adjacent side portions of the outer receiving hole 19a and the inner receiving hole 19b intersect each other and thereby communicate with each other.

The planetary gears 20 and 21 are housed in the housing holes 19a and 19b so as to be rotatable (spinned). One planetary gear 20 meshes with an internal gear (input member) 12d formed on the inner peripheral surface of the half body 12 at an open portion outside the accommodation hole 19a. The other planetary gear 21 meshes with a sun gear (output member) 22 that is rotatably provided in the housing 11 with its axis line coincident with the axis line L, at an open portion inside the accommodation hole 19b. Moreover, the planetary gears 20 and 21 mesh with each other at the communicating portions of the receiving holes 19a and 19b. Therefore, when the housing 11 is rotationally driven, the rotational torque input to the housing 11 is the internal gear 12d and the planetary gears 20 and 2.
1 is transmitted to the carrier 19 via 1 and further transmitted from the planetary gear 21 to the sun gear 22. The carrier 19 and the sun gear 22 rotate at the same speed when the planetary gears 20 and 21 do not rotate, but rotate differentially when the planetary gears 20 and 21 rotate.

  Next, the second differential gear mechanism 2 will be described. The carrier 19 and the sun gear 22 constitute a casing 23 of the second differential gear mechanism 2. Therefore, the casing 23 is divided into two parts (the carrier 19 and the sun gear 22) in the axis L direction, and the two parts are movable in the axis L direction. However, the carrier 19 and the sun gear 22 which are the two parts are actually prevented from moving in the direction of the axis L by the housing 11 and hardly move in the same direction.

  Inside the casing 23, a storage space 24 having a spherical shape and whose center is located on the axis L is formed. A support shaft 25 is provided inside the accommodation space 24. The support shaft 25 is arranged such that its axis is orthogonal to the axis L and passes through the center of the accommodation space 24. Both ends of the support shaft 25 are supported by the sun gear 22. Therefore, the support shaft 25 rotates integrally with the sun gear 22.

  In addition, a pair of pinion gears 26 and 26 and a pair of side gears 27 </ b> A and 27 </ b> B each formed of a bevel gear are accommodated inside the accommodation space 24. The pair of pinion gears 26 and 26 are rotatably fitted to both ends of the support shaft 25 in the accommodation space 24. The back surface of the pinion gear 25 is constituted by a part of a spherical surface having the same radius of curvature as the inner peripheral surface of the accommodating space 24, and the rear surface is in contact with the inner peripheral surface of the accommodating space 24. Therefore, the pair of pinion gears 25 and 25 are immovable in the directions away from each other.

  The pair of side gears 27 </ b> A and 27 </ b> B are arranged at one end and the other end of the accommodation space 24 in the direction of the axis L so that the respective axes coincide with the axis L. The rear surfaces of the side gears 27 </ b> A and 27 </ b> B are configured by a part of a spherical surface having the same radius of curvature as the inner peripheral surface of the accommodation space 24. One side gear 27 </ b> A is in contact with the inner peripheral surface of the accommodation space 24 constituted by the sun gear 22 on the back surface. The other side gear 27 </ b> B is in contact with the inner peripheral surface of the accommodation space 24 constituted by the carrier 19 on the back surface.

  Each side gear 27A, 27B meshes with a pair of pinion gears 26, 26. Therefore, when the sun gear 22 rotates, the pair of pinion gears 26 and 26 revolve around the axis L. Accordingly, the pair of side gears 27A and 27B are rotated about the axis L. At this time, the pair of side gears 27A and 27B rotate at the same speed if the pinion gear 26 does not rotate, and differentially rotates accordingly when the pinion gear 26 rotates.

  The hybrid differential gear device A is used as a center and a front differential. Therefore, the carrier 19 is connected to a rear differential (not shown), and the pair of side gears 27A and 27B are connected to left and right front wheels (not shown), respectively. Of course, the hybrid differential gear unit A can also be used as a center and a rear differential. In this case, the carrier 19 is connected to a front differential (not shown), and the side gears 27A and 27B are connected to the left and right rear wheels. (Not shown).

  In the hybrid differential gear device A having the above configuration, when the housing 11 is driven to rotate, the carrier 19 and the sun gear 22 are rotated. When the sun gear 22 rotates, the pinion gear 26 is rotationally driven via the support shaft 25, and the pair of side gears 27A and 27B that mesh with the pinion gear 26 are rotationally driven. At this time, since the teeth of the pinion gear 26 and the side gears 27A and 27B have pressure angles, the side gears 27A and 27B are pushed in a direction away from each other along the axis L by meshing with the pinion gear 26. As a result, the sun gear 22 is pressed into contact with the housing 11 (half body 12) via the washer 28, and the carrier 19 is pressed into contact with the housing 11 (half body 13) via the washer 29. Accordingly, when the first differential gear mechanism 1 is differentially rotated, a frictional resistance is generated between the housing 11, the carrier 19, and the sun gear 22. As a result, rotational torque is transmitted through the housing 11 from one of the carrier 19 and the sun gear 22 that rotates at a high speed to the other that rotates at a low speed. Therefore, the torque bias ratio between the carrier 19 and the sun gear 22 can be increased.

  Next, another embodiment of the present invention will be described. In the following embodiments, only components that are different from the above embodiments will be described, and the same components will be denoted by the same reference numerals, and description thereof will be omitted.

  FIG. 3 shows a second embodiment of the present invention. In the hybrid differential gear device B of this embodiment, a spline portion 31 a is formed on the outer periphery of the internal gear 31. An output gear 37 rotatably supported on the outer periphery of the housing 11 is fitted to the spline portion 31a so as not to rotate. Therefore, the rotational torque transmitted to the internal gear 31 is transmitted to the output gear 37, and the rotational torque is transmitted from the output gear 37 to the rear differential or the front differential.

  Further, in the hybrid differential gear device B, the casing 38 is constituted by the sun gear 22 and the half body 12 of the housing 11. That is, the sun gear 22 has a gear portion 22A that meshes with the planetary gear 30 and a casing constituent portion 22B in which one end portion (the right end portion in FIG. 5) is spline-coupled to the inner periphery of the gear portion 22A so as not to rotate. ing. An accommodation space 24 is defined by the other end of the casing component 22 </ b> B and the half 12. A support shaft 25 and a pinion gear 26 are provided in the casing component 22 </ b> B that partitions the housing space 24. Further, the side gear 27 is in contact with the inner surface of the casing constituting portion 22 </ b> B facing the accommodation space 24. The other side gear 27 </ b> A is in contact with the inner surface of the half 12 facing the accommodation space 24. Therefore, when the housing 11 is driven to rotate, the casing component 22B is pushed rightward in FIG. 5 by the meshing reaction between the side gear 27A and the pinion gear 26 and the meshing reaction force between the pinion gear 26 and the side gear 27B. Press contact with the half 13. Therefore, a frictional resistance is generated between the casing component 22 </ b> B and the half 13 of the housing 11 during differential rotation. Moreover, since the contact surfaces of the half 13 and the casing component 22B are tapered surfaces 13b and 22b, respectively, a larger frictional resistance is generated between the half 13 and the casing component 22b. A rotational torque having a magnitude corresponding to the frictional resistance is transmitted from one of the internal gear 31 and the sun gear 22 that rotates at a high speed to the other that rotates at a low speed. Thereby, the torque bias ratio is increased.

  FIG. 4 shows a first reference example of the present invention. In the hybrid differential gear device C of this reference example, instead of the pair of planetary gears 20 and 21 of the hybrid differential gear device A, only one kind of planetary gear 30 is used, and the planetary gear 30 is a planetary gear. A plurality of gears 20 and 21 are used in correspondence to a plurality of pairs. And each planetary gear 30 is supported by the half body 12 of the housing 11 (input member) so that rotation is possible. Therefore, in the hybrid differential gear device C, the carrier 19 in the hybrid differential gear device A is not used. In addition, an internal gear (output member) 31 formed separately from the housing 11 is provided in the housing 11 so that its axis is aligned with the axis L and is rotatable. The internal gear 31 is in mesh with the planetary gear 30, and the planetary gear 30 is also in mesh with the sun gear (output member) 22. Therefore, when the housing 11 is driven to rotate, the internal gear 31 and the sun gear 22 are rotated. As will be apparent, the housing 11, the planetary gear 30, the internal gear 31 and the sun gear 22 constitute the first differential gear mechanism 1.

  The end of the internal gear 31 on the half body 13 side is fitted so that the outer periphery of the intermediate member 32 rotates integrally. On the inner periphery of the intermediate member 32, an output cylinder 33 whose axis is aligned with the axis L is fitted in a non-rotatable manner. Therefore, the rotational torque transmitted from the housing to the internal gear 31 via the planetary gear 30 is transmitted to the output cylinder 33 via the intermediate member 32. Then, it is transmitted from the output cylinder 33 to the rear differential or the front differential.

  Further, in the hybrid differential gear device C, a casing (casing of the second planetary gear mechanism 2) 34 corresponding to the casing 23 of the hybrid differential gear device A is the central portion of the half body 12 of the housing 11 and the sun. The gear 22 and the output cylinder 33 are configured. That is, the casing 34 is divided into three in the direction of the axis L, and the accommodation space 24 is configured by three portions. Of the parts that define the housing space 24, the pinion gear 26 is in contact with the part (intermediate part) constituted by the sun gear 22, and the side gear 27 </ b> A is provided at the part (side part) constituted by the half body 12. The side gear 27 </ b> B is in contact with the portion (side portion) that is in contact with the output cylinder 33. Here, the output cylinder 33 is supported by the housing 11 so as to be movable in the direction of the axis L. Therefore, when a thrust force directed from the side gear 27A side to the side gear 27B side acts on the side gear 27B due to the engagement of the pinion gear 26 and the side gear 27B, the output cylinder 33 comes into pressure contact with the half body 13 of the housing 11 via the washer 35. Therefore, when the internal gear 31 and the sun gear 22 are differentially rotated, a frictional resistance is generated between the half body 13 and the output cylinder 33, and a rotational torque having a magnitude corresponding to the frictional resistance is generated between the internal gear 31 and the sun gear 22. Is transmitted from one rotating at a high speed to the other rotating at a low speed. This increases the torque bias ratio.

  In this reference example, the support shaft 25 is divided into three parts, that is, an intermediate part 25 a whose length is substantially equal to the inner diameter of the accommodation space 24, and two end parts 25 b and 25 b that fit into the support hole 22 a of the sun gear 22. Has been. Thereby, the support shaft 25 can be easily assembled to the sun gear 22. Further, a center portion of the intermediate portion 25a is provided with a pair of branch shaft portions (not shown) orthogonal to the axis line of the intermediate portion 25a and the axis L, and the pinion gear 26 is also rotatable on each branch shaft portion. Is provided. That is, in this embodiment, four pinion gears 26 are provided. Of course, all the pinion gears 26 mesh with the side gears 27A and 27B.

  FIG. 5 shows a second reference example of the present invention. Also in the hybrid differential gear device D of this reference example, the casing 34 of the second differential gear mechanism 2 is divided into three parts in the direction of the axis L, and the casing 34 is composed of a central portion (side portion) of the half body 12 and a cylinder. A holding portion (intermediate portion) 36 and a part (side portion) of the sun gear 22 are formed. The holding portion 36 is splined so as to rotate integrally with the internal gear 31. The holding portion 36 is provided with a support shaft 25. Therefore, the pinion gear 26 is in contact with the inner peripheral surface of the holding portion 36 that partitions a part of the accommodation space 24. Of course, the side gear 27 </ b> A is in contact with the central portion of the half body 12 that defines the accommodation space 24, and the side gear 27 </ b> B is in contact with the sun gear 22 that defines the accommodation space 24. Therefore, in this hybrid differential gear device C, when the housing 11 is driven to rotate, the sun gear 22 is pressed against the housing 11 via the washer 35. As a result, the torque bias ratio is increased.

  As is clear from the above description, in this hybrid differential gear device D, the holding portion 36 is non-rotatably connected to the internal gear 31 that is one output member, and the rotation of the sun gear 22 that is the other output member is the rear differential or the front. It is output to the differential. A planetary gear 30 is supported on the half 13. Other configurations are the same as those of the hybrid differential gear device C.

In addition, this invention is not limited to said embodiment, It can change suitably.
For example, in the above-described embodiment, the first differential gear mechanism 1 is configured so that the internal gear 12d (31), the planetary gears 20 and 21 (30) meshing with the internal gear 12d (31), and the sun meshing with the planetary gears 20 and 21 (30). The gear 22 comprises a housing that is rotationally driven, such as that described in JP-A-10-220556, at least a pair of planetary gears that are rotatably provided in the housing and mesh with each other, You may comprise from a pair of side gear which meshes with a planetary gear, respectively. In this case, the housing is also used as the input member, and the pair of side gears is the pair of output members.
Further, the input member in each of the above embodiments can be an output member, and one of the pair of output members can be an input member. For example, in the embodiment shown in FIGS. 1 and 2, the internal gear 12d (housing 11) is an input member, and the carrier 19 and the sun gear 22 are output members. However, the carrier 19 is an input member, It is also possible to use the gear 12d and the sun gear 22 as output members.

It is sectional drawing which follows the YY line of FIG. 2 which shows 1st Embodiment of this invention. It is sectional drawing which follows the XX line of FIG. It is sectional drawing similar to FIG. 1 which shows 2nd Embodiment of this invention. It is sectional drawing similar to FIG. 1 which shows the 1st reference example of this invention. It is sectional drawing similar to FIG. 1 which shows the 2nd reference example of this invention.

Explanation of symbols

A hybrid differential gear device B hybrid differential gear device 1 first differential gear mechanism 2 second differential gear mechanism 11 housing 12d internal gear (input member)
19 Carrier (output member)
20 planetary gear 21 planetary gear 22 sun gear (output member)
23 casing 26 pinion gear 27A side gear 27B side gear 30 planetary gear 31 internal gear (output member)
34 Casing

Claims (3)

An input member that is rotationally driven, a pair of output members that are rotated by the input member via a planetary gear, a first differential gear mechanism that includes a housing incorporating the input member and the pair of output members, and the housing A second casing having a casing provided therein, a pinion gear rotatably provided in the casing, and a pair of side gears rotatably provided with their axes aligned with each other inside the casing. In a hybrid differential gear device including a differential gear mechanism,
The casing is divided into two in the axial direction of the side gear, and among the parts of the casing divided into two, one portion that supports the pinion gear is rotatably provided in the housing, and the pair of pairs A portion of the casing that is non-rotatably connected to one of the output members and supports one of the pair of side gears is formed in the axial direction of the side gear that is generated by the engagement of the pinion gear and the side gear. The pair of side gears can be moved in the axial direction so that a frictional resistance is generated between the portion and the housing when the portion is rotated by the pressing force of the portion. Hybrid differential gear unit. The casing is divided into a part supporting the pinion gear and one side gear and a part supporting the other side gear, and the part supporting the pinion gear and one side gear is movable in the axial direction of the side gear. 2. The hybrid differential gear device according to claim 1, wherein a part of the housing is also used as a part for supporting the other side gear. The first differential gear mechanism includes an internal gear, a carrier, and a sun gear whose axes are aligned with each other, and a planetary gear that is rotatably provided on the carrier and meshes with the internal gear and the sun gear. The hybrid differential gear device according to claim 1, wherein any one of the internal gear, the carrier, and the sun gear is used as the input member, and the remaining two are used as the output member.

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