• 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:
    SHAFT ASSEMBLY WITH TORQUE DISTRIBUTION DRIVE MECHANISMS. These are a shaft assembly, an input member, a first planetary gear set, a differential assembly, and a second planetary gear set. The first planetary gear set has a first drive input that is driven by the input member. The differential assembly has a differential conveyor and first and second differential output members received on the differential conveyor. The second set of planetary gears has a planetary conveyor coupled to the differential conveyor for common rotation. A center gear of the first planetary gear set is non-rotatably coupled to a center gear of the second planetary gear set.
    公开号:BR112013000936B1
    申请号:R112013000936-5
    申请日:2011-07-14
    公开日:2021-08-31
    发明作者:Erik STEN
    申请人:E-Aam Driveline Systems Ab；
    IPC主号:
    专利说明:

    CROSS REFERENCE TO RELATED ORDERS
    [001] This patent application claims priority from Utility Patent Application Serial Number US 13/182,153 filed July 13, 2011, entitled "Axle Assembly With Torque Distribution Drive Mechanism", Provisional Patent Application Serial Number US 61/364,072, filed July 14, 2010, entitled "Torque Distribution Drive Mechanism" and Provisional Patent Application Serial Number US 61/468,809 filed March 29, 2011, entitled "Torque Distribution Drive Mechanism". Descriptions of these patent applications are hereby incorporated by reference as fully set out in detail herein. FIELD
    [002] The present description refers to an axle assembly and a vehicle that has a torque distribution drive mechanism. BACKGROUND OF THE DESCRIPTION
    [003] One means of correcting or reducing understeer or oversteer slippage in a vehicle is a torque vectoring differential (TVD). TVDs are typically electronically controlled differentials that are able to create a moment about a vehicle's center of gravity independent of the vehicle's wheel speed that would be employed to correct or reduce understeer or oversteer slip.
    [004] U.S. Patent 7,491,147 discloses a motor driven DTV that employs a pair of speed control mechanisms that are disposed on opposite sides of a differential mechanism. Each speed control mechanism comprises a gear reduction (cog) and a friction clutch. The gear reduction transmits rotary power from a differential box in the differential mechanism to the friction clutch, and from the friction clutch to an associated output rod (shaft).
    [005] Similarly, U.S. Patent 7,238,140 discloses a motor-driven DTV that employs a pair of torque deviators that are disposed on opposite sides of a differential mechanism. Each torque diverter comprises a gear reduction and a magnetic particle brake. The gear reduction transmits rotary power from a differential box of the differential mechanism to an output member that is coupled to an associated shaft output rod for rotation therewith. The magnetic particle brake is configured to selectively brake the gear reduction output member.
    [006] U.S. Patent Application Publication 2010/0323837 discloses an electrically driven TVD that has a pair of planetary transmissions, an electric motor, and a sleeve that controls the operation of the planetary transmissions. The TVD can be operated in a first mode in which the TVD is configured as an open differential that is driven by the electric motor and in a second mode in which the TVD produces a torque vectoring output.
    [007] Although such settings can be effective to realize a torque vectoring function in which a rotating power can be reallocated across the differential mechanism from one shaft rod to another, TVDs are nevertheless susceptible to improvement. SUMMARY OF DESCRIPTION
    [008] This section provides a brief overview of the description and is not a complete description of its entire scope or all of its features.
    [009] In one form, the present teachings provide a shaft assembly with an input member, a first planetary gear set, a differential mount, and a second planetary gear set. The first planetary gear set has a first transmission input that is driven by the input member. The differential assembly has a differential conveyor and first and second differential output members received on the differential conveyor. The second planetary gear set has a planetary conveyor coupled to the differential conveyor for common rotation. A center gear of the first planetary gear set is not pivotally coupled to a center gear of the second planetary gear set.
    [010] In another form, the present teachings provide a shaft assembly with an input member, a first planetary gear set, a differential mount, and a second planetary gear set. The first planetary gear assembly has a first drive input, a first center gear, a first ring gear, a plurality of first planetary gears, and a first planetary conveyor. The first transmit input is triggered by the input member. The first planetary gears are meshed with the first center gear and the first ring gear. The first planetary conveyor supports the first planetary gears for rotation. The differential assembly has a differential conveyor and first and second output members that are received on the differential conveyor. The second planetary gear set has a second planetary conveyor coupled to the differential conveyor for common rotation. The input member, first planetary gear set, and second planetary gear set are disposed on a common axial end of the differential carrier. The shaft assembly is operable in a mode in which the first and second planetary conveyors are pivotally decoupled from each other.
    [011] The first planetary gear set has a first transmission input that is driven by the input member. The differential assembly has a differential conveyor and first and second output members received on the differential conveyor. The second planetary gear set has a planetary conveyor coupled to the differential conveyor for common rotation. The input member, first planetary gear set, and second planetary gear set are disposed on a common axial end of the differential carrier.
    [012] In another form, the present teachings provide a shaft assembly that includes a motor, an input member driven by the motor, a differential assembly, a transmission and a displaceable element. The differential mount has a differential conveyor and differential first and second outputs received in the differential box. The transmission receives rotating power from the input member. The displaceable element is capable of axially moving between a first position and a second position. Positioning the displaceable element in the first position couples the transmission to the differential assembly to establish a torque vectoring mode in which the transmission applies an equivalent torque, but oppositely directed to the first and second differential outputs. Positioning the displaceable element in the second position couples the transmission to the differential mount to directly drive the differential conveyor.
    [013] In yet another form, the present teachings provide an actuator for linear displacement of a part in a mechanism that is switchable between at least two modes. The actuator includes an input member arranged to be operably coupled to a drive member, an output member arranged to be operably coupled to the switch, and a conversion member for converting a rotary motion of the drive member into a linear movement of the commutator. The converting member includes a cylindrical cam having a cam groove extending along at least a portion of a periphery of the cam, and a cam follower arranged to move in the cam groove. The cam is operably coupled to the input member, and the cam follower is operably coupled to the output member. The groove includes a first groove portion extending parallel to a transverse plane that is perpendicular to a longitudinal axis of the cam, a second groove portion extending parallel to the transverse plane, and a third groove portion extending between the first and the second groove portions, and extend in a direction along the periphery of the cam with the formation of an angle of more than 0° with respect to the transverse plane.
    [014] Other areas of applicability will become apparent from the description provided in this document. The description and specific examples in this summary are for illustrative purposes only and are not intended to limit the scope of this description. BRIEF DESCRIPTION OF THE DRAWINGS
    [015] The drawings described in this document are for illustrative purposes only of selected modalities and not of all possible implementations, and are not intended to limit the scope of this description.
    [016] Figure 1 diagrammatically illustrates a cross-sectional view of a torque distribution drive mechanism according to a first mode; Figure 2 diagrammatically illustrates a cross-sectional view of a torque distribution drive mechanism operable in many modes according to a second embodiment; Figure 3 diagrammatically illustrates a cross-sectional view of a torque distribution drive mechanism operable in many modes according to a third embodiment. Figure 4 is an exploded view of an actuator according to an embodiment of the description; Figure 5 is a partially disassembled view of the actuator of Figure 4; Figure 6 is a perspective view of the actuator of Figure 6; Figure 7 diagrammatically illustrates a cross-sectional view of a torque distribution drive mechanism according to a fourth embodiment; Figure 8 is a perspective view of a portion of the torque distribution drive mechanism of Figure 7; Figure 9 is an elevational rear view of a portion of the torque distribution drive mechanism of Figure 7; and Figure 10 is a perspective view of a portion of the torque distribution drive mechanism of Figure 7.
    [017] Corresponding reference numerals indicate corresponding parts throughout the various views of the drawings. DETAILED DESCRIPTION
    [018] Referring to Figure 1, a shaft assembly constructed in accordance with the teachings of the present description is generally indicated by reference number 10. The shaft assembly 10, which could be a front shaft assembly or a front shaft assembly. rear axle of a 12 vehicle, for example. The shaft assembly 10 can include a torque distribution drive mechanism 14a that can be used to transmit torque to a first output member 16 and a second output member 18, which are illustrated as being the first and second output rods. axis, respectively, in the present example. For example, the first output member 16 can be coupled to a left wheel 20 and the second output member 18 can be coupled to a right wheel 22 of the axle assembly 10. In particular, as explained further below, the drive mechanism 14a torque distribution can be used for torque vectoring, that is, to generate a torque difference between the first and second output members 16 and 18.
    [019] The torque distribution drive mechanism 14a may comprise a double planetary gear assembly 30 and a drive member 32.
    [020] The double planetary gear assembly 30 may be coaxially armed with respect to the first and second output members 16 and 18 and/or a differential assembly 36. The double planetary gear assembly 30 may comprise a first planetary gear assembly 40 and a second planetary gear set 42. The first and second planetary gear sets 40 and 42 have identical gear ratios and can be configured such that one or more of the components of the first planetary gear set 40 is/are interchangeable with associated component(s) of the second planetary gear assembly 42.
    [021] The first planetary gear assembly 40 may comprise a first center gear 50, a plurality of first planetary gears 52, a first ring gear 54, and a first planetary carrier 56. The first center gear 50 may be a generally structure hollow that can be concentrically set around the first output member 16. The first planetary gears 52 may be circumferentially spaced around the first center gear 50 such that the indentations of the first planetary gears 52 mesh with the indentations of the first center gear 50. Likewise, the first ring gear 54 may be arranged concentrically around the first planetary gears 52 such that the indentations of the first planetary gears 52 networkly engage the indentations in the first planetary gear. ring 54. The first ring gear 54 can be arranged g in a transmission housing 58 that can be non-rotatably coupled to a differential housing 60 that houses the differential assembly 36. The first planetary conveyor 56 can include a first conveyor body 62 and a plurality of first pins 64 that can be fixedly coupled to the first conveyor body 62. The first conveyor body 62 may be coupled to the first output member 16 in such a way that the first conveyor body 62 and the first output member 16 pivot together. Any suitable means for coupling the first conveyor body 62 to the first output member 16 may be employed, including welds and corresponding indentations or grooves. Each of the first pins 64 may be received in one of the associated first planet gears 52 and may support one of the associated first planet gears 52 for rotation about a longitudinal axis of the first pin 64.
    [022] The second planetary gear assembly 42 may comprise a second center gear 70, a plurality of second planetary gears 72, a second ring gear 74, and a second planetary carrier 76. The second center gear 70 may be a generally structure hollow that can be concentrically set around first output member 16. Second center gear 70 may be non-rotatably coupled to first center gear 50 (e.g., first and second center gears 50 and 70 may be formed integrally and unitarily). The second planet gears 72 may be circumferentially spaced around the second center gear 70 such that the indentations on the second planet gears network with the indentations of the second center gear 70. The second ring gear 74 may be arranged so concentric around the second planet gears 72 such that the indentations of the second planet gears 72 mesh with the indentations in the second ring gear 74. The second ring gear 74 may be non-rotatably coupled to the transmission housing 58. The second planetary conveyor 76 can include a second conveyor body 82 and a plurality of second pins 84 that can be fixedly coupled to the second conveyor body 82. The second conveyor body 82 can be coupled to a housing or differential conveyor 83 of the differential mount 36 such that the second transposing body r 82 and differential conveyor 83 rotate together. Each of the second pins 84 can be received in one of the associated second planet gears 72 and can support one of the associated second planet gears 72 for rotation about a longitudinal axis of the second pin 84.
    [023] The first and second planetary gear sets 40 and 42 can be aligned together around a common longitudinal axis (i.e., a longitudinal axis that can extend through the first and second center gears 50 and 70) and can be moved axially together along the common longitudinal axis 85.
    [024] The drive member 32 may be any means of providing a rotary input to the double planetary gear assembly 30, such as an electric or hydraulic motor, and may be employed to drive an input member 86 that transmits rotary power to a transmission input of the first planetary gear set 40. In the example provided, the transmission input is integral with the first ring gear 54, and the input member 86 is coupled to the first ring gear 54 for common rotation and includes a plurality of indentations that mesh into indentations of a reduction gear 88 which is mounted on an output rod 90 of the drive member 32. The input member 86 may be a separate component that can be non-rotatably coupled to the first ring gear 54, but in the example provided, the input member 86 and the first ring gear 54 are unitarily formed as a single distinct component.
    [025] In addition to the differential housing 60 and the differential conveyor 83, the differential assembly 36 may include means for transmitting rotary power from the differential conveyor 83 to the first and second output members 16 and 18. The rotary power transmission means may include a first differential output 100 and a second differential output 102. In the particular example provided, the rotating power transmission means comprises a differential gear assembly 104 which is housed in the differential conveyor 83 and which has a first gear side 106, a second side gear 108, a cross pin 110, and a plurality of pinion gears 112. The first and second side gears 106 and 108 may be rotatably disposed about a pivotal axis of the differential conveyor 83 and may comprising the first and second differential outputs 100 and 102, respectively. First output member 16 can be coupled to first side gear 106 for common rotation, while second output member 18 can be coupled to second side gear 108 for common rotation. Cross pin 110 may be pivotally armed on differential carrier 83 generally perpendicular to the pivot axis of differential carrier 83. Pinion gears 112 may be pivotally armed on cross pin 110 and meshed with first and second side gears 106 and 108 .
    [026] Although differential assembly 36 has been illustrated employing skewed pinions and side gears, it will be appreciated that other types of differential mechanisms can be employed, including differential mechanisms that employ a helical pinion and side gear sets or planetary gears.
    [027] Optionally, the differential assembly 36 can be coupled to a main or primary driver of the vehicle 12. In the particular example provided, the primary driver of the vehicle comprises a motor mechanism 120 that is employed to drive the differential assembly 36. thereafter, a rotary power produced by the motor mechanism 120 can be transmitted in a conventional manner to the differential conveyor 83 to drive the first and second output members 16 and 18 (that is, by means of the differential conveyor 83 and the set of differential gear 104). In this way, the drive member 32 can serve as a complement to the vehicle's primary driver 12 such that when an auxiliary torque is generated simultaneously by the drive member 32, the auxiliary torque will be superimposed on the first and second induced output torques. by prime mover as further explained below.
    [028] When the drive member 32 is activated (that is, when the output rod 90 of the drive member 32 rotates in the example provided), the drive member 32, the reduction gear 88 and the input member 86 can cooperating to apply a rotary power to the first ring gear 54 of the first planetary gear set 40. The rotary power received by the first ring gear 54 is transmitted via the first planetary gears 52 and the first planetary conveyor 56 to the first planetary member. output 16, while an opposite reaction is applied to the first center gear 50 such that the first center gear 50 rotates in a direction that is opposite the first planetary conveyor 56. A rotation of the first center gear 50 causes a corresponding rotation of the second center gear 70 to thereby drive the second planetary gears 72. By the fact that the second ring gear 74 is fixed Rotationally attached to the transmission housing 58, a rotation of the second planetary gears 72 causes a rotation of the second planetary conveyor 76 in a direction that is opposite to the direction of rotation of the first planetary conveyor 56. Hence, the magnitude of the rotary power (this ie, torque) that is transmitted from the second planetary conveyor 76 to the differential conveyor 83 (and through the differential assembly 36 to the second output member 18) is equivalent, but opposite to the magnitude of the rotating power (ie, torque) that is transmitted from the first planetary carrier 56 to the first output member 16.
    [029] Thus, as a result, the torque induced by the drive member 32 to the first and second output members 16 and 18, respectively, is counter-directed. Furthermore, since the first and second planetary gear sets 40 and 42 are operably coupled via the differential assembly 36, the magnitude of the torque induced in the first and second output members 16 and 18 is substantially equivalent. For example, if a positively directed torque is transmitted to the first output member 16 (by rotating the output rod 90 of the drive member 32 in a first rotational direction), an equivalent negative torque is transmitted to the second output member 18 Similarly, if a negatively directed torque is transmitted to the first output member 16 (by rotating the output rod 90 of the drive member 32 in a second direction of rotation opposite the first direction of rotation), a positive torque equivalent is transmitted to the second output member 18. In other words, the torque distribution drive mechanism 14a can be employed to generate a torque difference between the first and second differential outputs 100 and 102, which is communicated to the left wheels and right 20 and 22, respectively, through the first and second output members 16 and 18, respectively.
    [030] In situations where the drive member 32 is activated when a rotating power is transmitted from the primary driver (ie motor mechanism 120 in the example illustrated) to the differential mount 36, the torque transmitted by the torque distribution drive mechanism 14a will act as a displacement torque that is superimposed on the input torque transmitted to the shaft 10 assembly of the prime mover. In other words, the input torque of the primary driver is distributed via the differential assembly 36 such that a first driver torque is applied via the first differential output 100 to the first output member 16 and a second torque of drive is applied via the second differential output 102 to the second output member 18, while a supplemental torque induced by the drive member 32 is distributed via the double planetary gear assembly 30 such that a first torque of vectoring is applied to the first output member 16 and a second vectoring torque (which is equivalent to and opposite to the first vectoring torque in the example provided) is applied to the second output member 18 (via differential assembly 36). The useful torque acting on the first output member 16 is the sum of the first driver torque and the first vectoring torque, while the useful torque acting on the second output member 8 is the sum of the second driver torque and the second vectoring torque.
    [031] As an example, the torque distribution drive mechanism 14a can subtract a torque from the left wheel 20 and add a corresponding torque to the right wheel 22 when motor vehicle 12 makes a left turn, and can subtract a torque of the right wheel 22 and add a corresponding torque to the left wheel 20 when motor vehicle 12 turns to the right to improve vehicle 12's turning behavior and decrease its turning radius.
    [032] Those of skill in the art will appreciate that the configuration of the double planetary gear set 30 causes the first and second center gears 50 and 70 to experience the highest rotational speed, while the first ring gear 54 rotates at in a sense, at a slower rotational speed, and the first and second planetary conveyors 56 and 76 rotate at a rotational speed that is slower than that of the first ring gear 54. Thus, a favorable gear ratio, such as a gear ratio of around 1:1.5 to about 1:2.0, can be achieved between the first ring gear 54 and the first output member 16. As a result, the size of the gears of the set of 30 double planetary gear can be made small. For example, the diameter of the first and second planetary gears 52 and 72 can be as small as about 30 mm. In this way, the size of the double planetary gear assembly 30 can be small, and thus the torque distribution drive mechanism 14a can be made compact and light.
    [033] Drive member 32 is intended to be activated (eg, automatically or on a demand basis) when vehicle 12 turns. During a straight-line steering, the drive member 32 is then not activated to allow the vehicle 12 to be propelled in a forward direction by the motor mechanism 120. In such a situation, the differential mount 36, which receives input torque from the motor mechanism 120, transmits substantially equivalent torque to the first output member 16 and the second output member 18. In turn, substantially equivalent torque is transmitted to the first and second planetary conveyors 56 and 76 which rotate with substantially equivalent speed. As a consequence, and due to the identical planetary gear sets 40 and 42, there will be no relative motion between the first and second ring gears 54 and 74, which means that almost no effect or torque is transferred to the first and second gears. in ring 54 and 74. In other words, neither the first ring gear 54 nor the second ring gear 74 will rotate. In this way, the output rod 90 of the drive member 32 will not move and losses during a straight-line direction are thereby minimized.
    [034] Although the input member 86 has been illustrated and described as directly engaging the reduction gear 88, it will be appreciated that one or more steps could be disposed between the input member 86 and the reduction gear 88 or the lowering member. input 86 could be driven directly by the drive member 32.
    [035] Referring to Figure 2, another shaft assembly constructed in accordance with the teachings of the present description is generally indicated by reference numeral 10b. The 10b shaft assembly may be generally similar to the 10 shaft assembly of Figure 1 except as noted herein. In this example, the shaft assembly 10b comprises a torque distribution drive mechanism 14b that is selectively operable in a plurality of operating modes that include a torque vectoring mode, a drive mode, and a neutral mode. The torque distribution drive mechanism 14b may be structurally similar to the torque distribution drive mechanism 14a of Figure 1, except that the input member 86b is rotatable relative to the first ring gear 54b and an actuator 150 is employed to control the operational state of the torque distribution drive mechanism 14b. The input member 86b may comprise a crown gear which can be rotatably armed about the first output member 16 and the first planetary gear assembly 40b. Actuator 150 can include a displacement sleeve 152 that can form the transmission inlet. The displacement sleeve 152 may have an indented outer surface 154, which is non-rotatably but axially and slidably engaged with a correspondingly indented inner surface 156 of the inlet member 86b, a set of first inner indentations 160 , matingly engageable with corresponding indentations 162 formed on the first ring gear 54b, and a set of second inner indentations 164 correspondingly engageable with corresponding indentations 166 formed on the second planetary conveyor 76b.
    [036] In torque vectoring mode, the displacement sleeve 152 can be positioned in a first position to couple the input member 86b to the first ring gear 54b (by means of engaging the set of first inner indentations 160 to the indentations 162 in the first ring gear 54b) such that the input member 86b, the displacement sleeve 152 and the first ring gear 54b rotate together. It will be appreciated that the set of second inner indentations 164 is disengaged from the indentations 166 on the second planetary conveyor 76b when the displacement sleeve 152 is in the first position. Accordingly, it will be appreciated that an operation of the torque distribution drive mechanism 14b in the torque vectoring mode is substantially similar to the operation of the torque distribution drive mechanism 14a (Figure 1). In that regard, the drive member 32 can be selectively activated to induce a torque difference between the first and second output members 16 and 18 as explained above.
    [037] In drive mode, the displacement sleeve 152 can be positioned in a second position to couple the input member 86b to the second planetary conveyor 76b (by means of engaging the set of second inner indentations 164 with the indentations 166 in the second planetary conveyor 76b) such that a rotary power supplied by drive member 32 is inserted into differential conveyor 83 and applied to first and second output members 16 and 18 via differential assembly 36. It will be appreciated that the set of first indentations Internal 160 in shift sleeve 152 can be disengaged from indentations 162 in first ring gear 54b when shift sleeve 152 is in the second position. It will also be appreciated that a rotary power provided by drive member 32 when torque distribution drive mechanism 14b is operated in drive mode is employed for propulsive power to propel (or help propel) vehicle 12.
    [038] In neutral mode, displacement sleeve 152 can decouple input member 86b from first ring gear 54b and second planetary conveyor 76b such that input member 86b is decoupled from first planetary gear set 40b, the second planetary gear assembly 42b, and the differential conveyor 83. In the example provided, the shift sleeve 152 may be positioned in a third position between the first and second positions such that the first and second inner indentation sets 160 and 164 are axially disposed therebetween and disengaged from indentations 162 on the first ring gear 54b and from indentations 166 on the second planetary conveyor 76b. Consequently, a placement of the shift sleeve 152 in the third position decouples the drive member 32 from the first planet gear assembly 40b, the second planet gear assembly 42b, and the differential carrier 83.
    [039] Referring to Figure 3, yet another shaft assembly constructed in accordance with the teachings of the present description is generally indicated by reference numeral 10c. The 10c shaft assembly may be generally similar to the 10b shaft assembly of Figure 2 except as noted herein. In this example, the shaft assembly 10c comprises a torque distribution drive mechanism 14c that is selectively operable in a plurality of operating modes that include a torque vectoring mode, a drive mode, a neutral mode, and a drive mode. of low speed. The torque distribution drive mechanism 14c may be structurally similar to the torque distribution drive mechanism 14b of Figure 2, except that the displacement sleeve 152c may have a third set of inner indentations 170 that can be selectively engaged with the indentations 172 of an indented element 174 that is coupled to the first and second center gears 50 and 70 for rotation therewith. The set of third internal indentations 170 are not engaged to any other structure when the torque distribution drive mechanism 14c is operated in the torque vectoring, drive and neutral modes and as such, the operation of the torque distribution drive mechanism 14c is substantially similar to the torque distribution drive mechanism operation of Figure 2 in these modes.
    [040] In the low speed drive mode, however, the shift sleeve 152c can be positioned in a fourth position to couple the input member 86b to the first and second center gears 50 and 70 (by means of the set engagement from third inner indentations 170 to indentations 172 in element 174) such that inlet member 86b, displacement sleeve 152c, element 174, and first and second center gears 50 and 70 rotate together. In this mode, the second planetary gear set 42b is employed as a gear reduction which causes the second planetary conveyor 76b to rotate at a rotational speed that is less than the rotational speed of the second center gear 70. It will be appreciated that sets of first and second inner indentations 160 and 164 are disengaged from indentations 162 in first ring gear 54b and indentations 166 in second planetary conveyor 76b when displacement sleeve 152c is in the fourth position.
    [041] Those of skill in the art will appreciate that a rotary power is inserted into the double planetary gear assembly 30b at different locations when a torque distribution drive mechanism 14c is operated in drive mode and low speed drive. In that regard, a rotary power is input to the second planetary conveyor 76b in drive mode, and input to first and second center gears 50 and 70 in low speed drive. Accordingly, it will be appreciated that the differential conveyor 83 will rotate at a slower rotational speed (for a given rotational speed of the output rod 90 of the drive member 32) in the low speed drive as compared to the drive mode. In this regard, a rotation of the first and second center gears 50 and 70 when the torque distribution drive mechanism 14c is operated at the low speed drive will cause a corresponding rotation of the second planetary gears 72, which in turn drives the rotation of the second planetary conveyor 76 and the differential conveyor 83. In other words, a gear reduction is disposed between the rotary input (ie, the element 174) and the differential conveyor 83 when the torque distribution drive mechanism 14c is operated in the low speed drive, and no gear reduction is disposed between the rotary input (ie, the second planetary conveyor 76b) and the differential conveyor 83 when the torque distribution drive mechanism 14c is operated in the drive mode. .
    [042] The dimension of the displacement sleeve 152 in the axial direction and the width and spacing of the many sets of indentations can be selected in such a way that on most teeth one of the sets of internal indentations 160, 164 and 170 is allowed to engage the corresponding indentations 162, 166 and 172, respectively, at the same time. Additionally or alternatively, the offset diameters of the corresponding indentation sets may be differentially sized to allow certain indentations to slide over other indentations where engagements of those indentations are not desired. For example, the offset diameter of the set of second inner indentations 164 is greater than the offset diameter of the set of third inner indentations 170 so that the set of second inner indentations 164 can pass axially through the indentations 172 in the member. 174 which is rotatably coupled to the first and second center gears 50 and 70.
    [043] It is also possible to build a torque distribution drive mechanism that is operable only in drive and neutral modes. In such a case, the double planetary gear assembly 30 can be omitted as its functionality of generating counter-directed torques in torque vectoring mode and entering a reduced speed for differential conveyor 83 in low speed drive are not required.
    [044] In such a situation, the torque distribution drive mechanism may comprise a drive member, a crown gear operably coupled to the drive member, a switching member rotatably coupled to the crown gear to switch between the drive mode and the neutral gear mode, and a differential that is operably coupled to a first and a second output member. Shift sleeve 152 or other switching member may be arranged to engage the differential. In particular, the switching member may be arranged to engage a differential carrier of the differential. Furthermore, the switching member can be arranged to be in a position where it is decoupled from the differential.
    [045] Similar to the embodiments of Figures 2 and 3, disclosed above, the switching element may comprise a displacement sleeve pivotally coupled to the crown gear. Further, the switching element may comprise a radially extending indentation structure which is disposed on the shift sleeve in a radially inward direction and which is arranged to engage with a corresponding indentation structure on the outer surface of the differential carrier. The displacement sleeve can slide along the crown gear in an axial direction. By sliding the shift sleeve in the direction of the differential, the shift sleeve sprocket can engage with the corresponding stent frame on the differential carrier. In this way, the torque distribution drive mechanism is operable in high gear mode. By sliding the shift sleeve away from the differential, the shift member indentation structure disengages from the indentation structure on the outer surface of the differential carrier. In this way, the drive member will be in a neutral gear as it does not induce any torque to the differential.
    [046] An advantage with this construction is that it can be formed in a modular way. That is, the construction can be formed as a module that can easily be added to a differential on an existing transmission.
    [047] The switching element or travel sleeve in each of the last three examples can be moved axially by any desired actuator, including conventional displacement yoke actuators of the type that are commonly used in transfer cases. It will also be appreciated that one or more synchronizers may be incorporated with the shift sleeve to allow the shift sleeve to be actuated (e.g., via the first ring gear or the second planetary conveyor) prior to a member actuation of drive 32 such that the rotational speed of the displacement sleeve is corresponding to the rotational speed of the component to which the displacement sleeve is to be pivotally coupled.
    [048] Referring to Figure 4, an exemplary actuator 200 for translating a displacement sleeve is illustrated. Actuator 200 has an input member in the form of a swivel connection 202 to a drive member, such as a DC electric motor 210, Figure 6, or other suitable swivel insertion device. The swivel connection 202 generally comprises a swivel rod 300, which is connected to the motor 210. In addition, the actuator 200 has an output member 400 in the form of a piston or rod. A projection or protrusion 500 is attached to rod 400. Along a guide portion 600 of rod 400, a cross-section of rod 400 is not cylindrical.
    [049] A cylindrical cam 700 is disposed on the rotating rod 300. A cam groove 800 is formed around the cylindrical cam 700. The cam groove 800 is divided into three groove portions 800a, 800b, and 800c. A first groove portion 800a extends along and around the periphery of cam 700 in a direction parallel to a transverse plane 710 that is perpendicular to a longitudinal axis C of cam 700. A second groove portion 800b also extends along of the periphery of the cam 700 and around it in the direction parallel to the transverse plane 710. A third groove portion 800c extends along the periphery of the cam 700 and around the same between the first groove portion 800a and the second groove portion 800b, and extends in a direction that forms an angle of more than 0° with respect to the transverse plane. Thus, the first and second groove portions 800a and 800b are not inclined, that is, they have zero inclination in the axial direction of cam 700 and with respect to the transverse plane 702, while the third groove portion 800c tilts and extends axially along the longitudinal axis C of cam 700.
    [050] A first flange 900 and a second flange 901 are disposed one on each side of the cylindrical cam 700. A first through hole 91 in the first flange 900 and a second through hole 921 in the second flange 901 form a guide for the rod 400. The second through hole 921 forms a passage with a non-circular cross-section that corresponds to the cross-section of the guide portion 600 of the rod 400. A third through hole 931 of the first flange 900 and a fourth through hole 941 of the second flange 901 are disposed of. so that each receives a respective end of swivel rod 300, supported for rotation by respective roller bearings 951 and 961. Four spacing or spacing elements 971 are arranged to be placed between flanges 900 and 901.
    [051] Figure 5 illustrates how the parts of the actuator 200 are assembled. In particular, it can be seen that the protrusion 500 is fitted within the cam groove 800. As the cylindrical cam 700 is rotated by the motor 210, the protrusion 500 is forced to follow the groove 800. When the protrusion 500 moves axially of the first groove 800a through the third groove portion 800c and for the second groove portion 800b, the rod is displaced in a linear direction L. Thus, a movement of the cylindrical cam 700 in a rotary direction R is converted to a linear displacement in the direction linear L.
    [052] When protrusion 500 is positioned in the first portion of groove 800a, which has zero slope, an angle between the groove and rod is 90°. Therefore, protrusion 500 will have no axial or linear force applied to it and rod 400 will be held in that position. The first groove portion 800a corresponds to a first position of a switch 810 operably coupled to rod 400. In that first position, switch 810 ensures that displacement sleeve 152 (Figure 2) can be positioned in the third position to allow the torque distribution drive mechanism 14b (Figure 2) operates in drive mode.
    [053] If the motor 210 is started, the cylindrical cam 700 rotates in the direction of rotation R and the protrusion 500 is moved from the first groove portion 800a, along the third inclined groove portion 800c, to the second groove portion 800b , and through which to move rod 400 in the linear direction L. Since the second portion of groove 800b has zero inclination, protrusion 500 will have no axial or linear force applied to it and rod 400 will be held in that position since engine 210 is stopped. Thus rod 400 will stop moving and switch 810 will be held in a second position. In this second position, the switch ensures that the displacement sleeve 152 (Figure 2) can be positioned in the first position to allow the torque distribution drive mechanism 14b (Figure 2) to operate in torque vectoring mode.
    [054] The person skilled in the art will appreciate that a number of modifications of the modalities described herein are possible to deviate from the scope of the description, which is defined in the appended claims.
    [055] For example, the actuator 200 was described above in the context of a motor vehicle torque distribution mechanism 12, but such an actuator is equivalently useful in other constructions. The actuator can, for example, be used in a locking mechanism, where the different modes could correspond to a locked state and an unlocked state. Generally speaking, an actuator of the type described above can be used in any context in which a part must be moved linearly, quickly and accurately, and in which the displacement must be actuated by a drive member that provides an emission of rotation.
    [056] In the exemplary embodiment described above, the groove 800 has two portions of groove 800a and 800c without inclination. Naturally, more than two uninclined groove portions can be formed on cam 700, each uninclined groove portion corresponding to a position of the part that is connected to the rod, e.g. a switch. Thus, in a torque distribution drive mechanism, a groove with three non-tilted groove portions, and two inclined groove portions connecting the uninclined groove portions, can correspond to three different gear modes, such as one mode of propulsion, a torque vectoring mode, and a neutral gear mode.
    [057] Referring to Figures 7 to 10 of the drawings, another 10d axis assembly constructed in accordance with the teachings of the present description is illustrated. The shaft assembly 10d may include a torque distribution drive mechanism 14d which may be similar to the torque distribution drive mechanism 14a of Figure 1 except as noted. Therefore, reference numerals used in Figure 1 will be used to indicate corresponding elements in Figures 7 to 10.
    [058] Instead of the drive member 32 and the reduction gear 88 that are employed in Figure 1 (the drive member 32 and the reduction gear 88 are arranged around a rotary axis that is parallel to the rotary axes of the differential conveyor 83 and of the first planetary conveyor 56), the example of Figures 7 to 10 employs a drive member 32d and a reduction gear 88d which are disposed about a revolving axis 1300 which is perpendicular to the revolving axes 85 of the differential conveyor 83 and of the first planetary conveyor 56. For example, the rotary shaft 1300 may be orthogonal to a rotary shaft 1304 of a motor mechanism 120 (or other means for providing rotary power, such as an electric or hydraulic motor) and the rotary shafts 85 of the conveyor differential 83 and the first planetary conveyor 56. Motor mechanism 120 can drive an input pinion 1306 (for example, by means of a propeller shaft. trada)) which is networked with a ring gear 1308 which can be coupled to the differential conveyor 83 in a conventional manner.
    [059] Setting the torque distribution drive mechanism 14d in this way may be advantageous in some situations when space to accommodate the torque distribution drive mechanism in a vehicle is limited.
    [060] The 32d drive member can be any type of motor, such as an AC electric motor or a DC electric motor, and may have a 37d-1 output rod to which the 88d reduction gear can be coupled from. swivel way.
    [061] The reduction gear 88d may be a worm gear 1312 that can be meshed with a worm gear 1314. The worm gear 1314 can be pivotally coupled to the first ring gear 54d ( for example, formed on an outer surface of the first ring gear 54d). Auger 1312 and worm gear 1314 may be relatively small in size, but nevertheless provide a relatively large gear reduction ratio. Consequently, the drive member 32d can be configured to produce relatively high speed, low torque output and as such can be relatively smaller in diameter than the drive member 32 of Figure 1.
    [062] If desired, worm 1312 and worm gear 1314 can be configured to be self-locking when drive member 32d does not actively receive power to effectively lock differential assembly 36d to inhibit a speed differential between the first and second output members 16 and 18. In this regard, the locking of worm 1312 and worm gear 1314 inhibits a rotation of the first ring gear 54d. Since the second planetary conveyor 76d and the differential conveyor 83 are coupled for rotation, a rotation of the differential conveyor 83 (via rotation of the differential ring gear 1308 resulting from a rotation of the input pinion 1306) can provide a rotary input to the second planet conveyor 76d, which causes the second planet gears 72 of the second planet gear set 42 to rotate in the second ring gear 74 and to rotate the second center gear 70. A rotation of the second center gear 70 causes a rotation of the first gear center 50, and causes a rotation of the first planetary gears 52 of the first planetary gear set 40, which in turn causes the first planetary conveyor 56 to rotate. Since the first planetary conveyor 56 is coupled to the first output member 16, and since the first and second planetary gear sets 40 and 42 have identical gear reduction ratios, the first and second planetary conveyors 56 and 76 rotate thereto. proportion (ie, the proportion at which the differential conveyor 83 rotates). Therefore, the first output member 16 cannot rotate relative to the differential conveyor 83 so that the differential gear assembly 104 is locked to the differential conveyor 83.
    [063] In order for worm 1312 and worm gear 1314 to be self-locking, worm gear 1314 cannot back-drive worm 1312. As those skilled in the art will appreciate, the skill of the Locking worm 1312 and worm gear 1314 depends on many factors, including feed angle, pressure angle, and coefficient of friction, but often the analysis can be reduced to a rough estimate involving the coefficient of friction and the tangent of the feed angle (ie self-locking if the tangent of the feed angle < coefficient of friction).
    [064] With specific reference to Figures 7 and 10, the double planetary gear assembly 30 and the reduction gear 88d may be housed in a housing 1340 which may comprise a first housing housing 1342 and a second housing housing 1344 which are fixedly coupled together by means of a set of fasteners (not shown). Drive member 32d may be armed to a flange 1348 formed in first housing shell 1342. Seals 1352 may be employed to seal the interface between housing 1340 and first output member 16 and between housing 1340 and a portion of the second planetary conveyor 76d which is pivotally coupled to differential conveyor 83. In addition, a seal 1354 may be received in housing 1356 in which differential conveyor 83 is arranged to seal the interface between housing 1356 and portion of second planetary conveyor 76d which is pivotally coupled to the differential conveyor 83.
    [065] It will be appreciated that the above description is merely exemplary in nature and is not intended to limit the present description, its application or uses. Although specific examples have been described in the specification and illustrated in the drawings, it will be understood by those skilled in the art that various changes can be made and equivalents can be replaced by elements thereof without departing from the scope of the present description as defined in the claims. Furthermore, the mixing and matching of features, elements and/or functions between various examples are expressly contemplated in this document, even if not specifically shown or described, in a manner that a person skilled in the art would appreciate from this description, that features, elements and/or functions of one example may be incorporated into another example as appropriate, unless otherwise described above. Furthermore, many modifications can be made to adapt a particular situation or material to the teachings of the present description without departing from the essential scope of the same. Therefore, it is intended that the present description is not limited to the particular examples illustrated by the drawings and described in the descriptive report as the best mode currently contemplated to carry out the teachings of this description, however, it is intended that the scope of this description include any embodiments covered by the above description and the appended claims.
    权利要求:
    Claims (17)
    [0001]
    1. Shaft assembly (10, 10b, 10c, 10d) characterized in that it comprises: an input member (86, 86b, 1314); a first planetary gear set (40, 40b) having a first transmission input (54, 54b, 54d) that is driven by the input member (86, 86b, 1314); a differential assembly (36, 36d) having a differential carrier (83) and first and second differential output members (100, 102) received on the differential carrier (83); a second planetary gear set (42, 42b) having a planetary conveyor (76, 76b, 76d), which is coupled to the differential conveyor (83) for common rotation, and a ring gear (74); and a housing (58, 1340) in which the first planetary gear set (40, 40b) and the second planetary gear set (42, 42b) are received; wherein a center gear (50) of the first planetary gear set (40, 40b) is non-rotatably coupled to a center gear (70) of the second planetary gear set (42, 42b); and wherein the ring gear (74) of the second planetary gear assembly (42, 42b) is fixedly coupled to the housing (58, 1340).
    [0002]
    2. Shaft assembly (10, 10b, 10c, 10d) according to claim 1, characterized in that it further comprises a clutch (150) to selectively decouple the input member (86b) from the first input of transmission (54b).
    [0003]
    3. Shaft assembly (10, 10b, 10c, 10d) according to claim 2, characterized in that the clutch (150) is further operable to selectively couple the input member (86b) to the differential conveyor (83), so that the input member (86b) and the differential conveyor (83) rotate together.
    [0004]
    4. Shaft assembly (10, 10b, 10c, 10d) according to claim 2, characterized in that the clutch (150) is further operable to selectively lock the first and second planetary gear sets ( 40b, 42b), such that the first and second output members (100, 102) of the differential mount (36) pivot together.
    [0005]
    5. Shaft assembly (10, 10b, 10c, 10d) according to claim 1, characterized in that it further comprises a displacement sleeve (152) that is movable between a first position and a second position, and in that the shift sleeve (152) engages the inlet member (86b) and the planetary conveyor (76b) of the second planetary gear set (42b) when the shift sleeve (152) is positioned in the second position.
    [0006]
    6. Shaft assembly (10, 10b, 10c, 10d) according to claim 5, characterized in that the displacement sleeve (152) is movable in a third position in which the displacement sleeve (152) locks the first and second planetary gear sets (40b, 42b) so that the output members (100, 102) of the differential mount (36, 36d) rotate together.
    [0007]
    7. Shaft assembly (10, 10b, 10c, 10d) according to claim 6, characterized in that the displacement sleeve (152) couples the input member (86b) to the central gears (50, 70) of the first and second planetary gear sets (40b, 42b) for common rotation when the displacement sleeve (152) is in the third position.
    [0008]
    8. Shaft assembly (10, 10b, 10c, 10d) according to claim 5, characterized in that the displacement sleeve (152) is movable in a neutral position and that the input member (86b) is decoupled from the first planetary gear set (40b), second planetary gear set (42b), and differential conveyor (83) when the displacement sleeve (152) is moved to the neutral position.
    [0009]
    9. Shaft assembly (10, 10b, 10c, 10d) according to claim 5, characterized in that the displacement sleeve (152) couples the input member (86b) to a ring gear (54b) of the first planetary gear set (40b) when the displacement sleeve (152) is in the first position.
    [0010]
    10. Shaft assembly (10, 10b, 10c, 10d) according to claim 1, characterized in that it further comprises an electric motor (32, 32d) actuable-coupled to the input member (86b) through an auxiliary gear reduction (88, 88d).
    [0011]
    11. Shaft assembly (10, 10b, 10c, 10d) according to claim 10, characterized in that the auxiliary reduction comprises a worm (1312) and a worm gear (1314) in net engagement with the worm screw (1312).
    [0012]
    12. Shaft assembly (10, 10b, 10c, 10d) according to claim 1, characterized in that it further comprises a ring gear (1308) coupled to the differential conveyor (83) for common rotation between them.
    [0013]
    13. Shaft assembly (10, 10b, 10c, 10d) according to claim 1, characterized in that it further comprises a pair of shaft rods (16, 18), each of the shaft rods (16 , 18) being actionably coupled to an associated one of the output members (100, 102) of the differential assembly (36, 36d).
    [0014]
    14. Shaft assembly (10, 10b, 10c, 10d) according to claim 1, characterized in that the differential assembly (36, 36d) further comprises a plurality of pinion gears (112) which are mounted on the differential conveyor (83) and wherein the output members (100, 102) of the differential assembly (36, 36d) are side gears (106, 108) which are meshed with the pinion gears (112).
    [0015]
    15. Shaft assembly (10, 10b, 10c, 10d) according to claim 1, characterized in that a ring gear (54) of the first set of planetary gears (40, 40b) is coupled to the member of input (86b) for rotation with it.
    [0016]
    16. Shaft assembly (10, 10b, 10c, 10d) according to claim 1, characterized in that one of the shaft rods (16) is received through the central gears (50, 70) of the first and the second planetary gear sets (40, 40b, 42, 42b).
    [0017]
    17. Shaft assembly (10, 10b, 10c, 10d) according to claim 13, characterized in that a planetary conveyor (56) of the first planetary gear set (40) is coupled to one of the shaft rods (16) for common rotation.
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    同族专利:
    公开号 | 公开日
    US20120058855A1|2012-03-08|
    CN103119332B|2015-10-14|
    KR20180030234A|2018-03-21|
    KR101839168B1|2018-03-15|
    US8663051B2|2014-03-04|
    IN2013CN00389A|2015-07-03|
    WO2012007829A3|2012-05-18|
    WO2012007829A2|2012-01-19|
    EP2662595B1|2018-01-31|
    EP2593696B1|2017-08-30|
    KR20130042568A|2013-04-26|
    EP2593696A2|2013-05-22|
    KR101948491B1|2019-02-14|
    EP2662595A2|2013-11-13|
    RU2013106421A|2014-08-20|
    BR112013000936A2|2020-11-03|
    EP3273096A1|2018-01-24|
    EP2662595A3|2014-08-27|
    CN103119332A|2013-05-22|
    RU2569722C2|2015-11-27|
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    法律状态:
    2020-11-17| B06F| Objections, documents and/or translations needed after an examination request according [chapter 6.6 patent gazette]|
    2020-12-01| B06U| Preliminary requirement: requests with searches performed by other patent offices: procedure suspended [chapter 6.21 patent gazette]|
    2021-07-06| B09A| Decision: intention to grant [chapter 9.1 patent gazette]|
    2021-08-31| B16A| Patent or certificate of addition of invention granted [chapter 16.1 patent gazette]|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 14/07/2011, OBSERVADAS AS CONDICOES LEGAIS. PATENTE CONCEDIDA CONFORME ADI 5.529/DF, QUE DETERMINA A ALTERACAO DO PRAZO DE CONCESSAO. |
    优先权:
    申请号 | 申请日 | 专利标题
    US36407210P| true| 2010-07-14|2010-07-14|
    US61/364,072|2010-07-14|
    US201161468809P| true| 2011-03-29|2011-03-29|
    US61/468,809|2011-03-29|
    US13/182,153|2011-07-13|
    US13/182,153|US8663051B2|2010-07-14|2011-07-13|Axle assembly with torque distribution drive mechanism|
    PCT/IB2011/001637|WO2012007829A2|2010-07-14|2011-07-14|Axle assembly with torque distribution drive mechanism|
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