巴西专利BR102015008968B1 compact shaft assembly with locking differential

专利PDF首页>>巴西专利

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:
COMPACT AXLE ASSEMBLY WITH LOCK DIFFERENTIAL. A mounting shaft that has a carrier housing, a differential lock assembly, a differential bearing pair and an actuator assembly. The carrier housing includes a cavity. The differential lock assembly includes a differential box that is received in the cavity. A differential case includes a bearing bore in which an outer race of the differential bearing is received. The drive assembly includes a sleeve that is movable between a first sleeve position, in which it is configured to cause the locking differential assembly to operate in an unlocked mode, and a second sleeve position in which it is configured to make with the locking differential assembly to operate in a locked mode. The sleeve is at least partly radially in line with the differential bearing when the sleeve is in the first and / or second sleeve positions such that a plane of a plane perpendicular to the axis extends through both the sleeve and the bearing of the differential.
公开号:BR102015008968B1
申请号:R102015008968-6
申请日:2015-04-20
公开日:2021-02-17
发明作者:Gregory A. Marsh；Matthew T. Blakeman
申请人:American Axle & Manufacturing, Inc.；
IPC主号:

专利说明:

[0001] [001] This application claims the benefit of provisional application No. US61 / 983092, filed on April 23, 2014, the disclosure of which is incorporated by reference as if outlined in its entirety here. TECHNICAL FIELD
[0002] [002] The present disclosure relates to a compact shaft assembly with a locked assembly. FUNDAMENTALS
[0003] [003] This section provides background information related to the present disclosure that is not necessarily state of the art.
[0004] [004] In the off-road field, bundles of axles are perceived as providing advantages over other types of axle assembly when operating in certain types of terrain, such as when in gravel. These advantages include the perception of increased durability and the articulation of the axle assembly when crossing uneven terrain so that the position of the differential can be changed as a function of the position of the axle wheels in order to better avoid contact between the ground / an obstruction and the axle assembly portion that surrounds the differential. While the known axle bundles are satisfactory for the intended use, there remains a need in the art for a better axle bundle.
[0005] [005] For example, sets of axles for off-road use normally employ a set of locking differentials to inhibit speed differentiation between the wheels of an axle set. In known axle beam configurations, the locking mechanisms of the typically known differential locking sets increase the width of the central section of the axle housing. As will be seen, any increase in the center section of the axle housing creates an increased risk that the axle assembly will contact an obstruction when operating a vehicle in off-road conditions. SUMMARY OF THE INVENTION
[0006] [006] This section provides a general summary of the revelation, and is not a revelation understood in all its scope or all of its aspects.
[0007] [007] In one form, the present disclosure provides an axle assembly with an axle housing, a differential lock assembly, a cover and a driver assembly. The shaft housing has a center section that defines a cavity. The differential lock assembly is received in the cavity for rotation about an axis and has a differential box, first and second output members, and a locking element that moves mounted to the differential box. The cover is mounted to the center section to partially close an open side of the cavity. The cover defines a trigger opening that provides cover access to the cavity. The driver set includes a sleeve and a driver. The sleeve is mounted on the differential box and is movable along the axis between a first sleeve position and a second sleeve position. The driver is mounted to an external side of the cover and extends through the driver opening to wrap the sleeve. The driver is selectively configured to move the sleeve between the first and second sleeve positions. The differential locking set is configured to operate in an unlocked mode that allows differentiation of speed between the first and second output members when the sleeve is in the first sleeve position. The differential locking set is configured to be operated in a locked mode which prevents the speed differentiation between the first and second output members when the sleeve is in the second sleeve position.
[0008] [008] In another form, the present disclosure provides an axle assembly with an axle housing, a differential lock assembly, a differential bearing and a driver assembly. The shaft housing has a center section that defines a cavity. The locking differential assembly is received in the cavity and includes a differential case, first and second output elements, and a locking element that is movably mounted to the differential case. The differential case defines a bearing cylinder. The differential bearing has an outer bearing that is received in the bearing cylinder and enclosed in the differential case. The differential bearing supports a differential locking assembly for rotation about an axis relative to the shaft housing. The driver assembly has a sleeve and a driver. The sleeve is mounted on the differential box and is movable along the axis between a first sleeve position and a second sleeve position. The driver is attached to the shaft housing and engages the sleeve. The driver is selectively configured to move the sleeve between the first and second sleeve positions. The differential locking set is configured to operate in an unlocked mode that allows differentiation of speed between the first and second output members when the sleeve is in the first sleeve position. The differential locking set is configured to operate in a locked mode that prevents differentiation of speed between the first and second output members when the sleeve is in the second sleeve position. At least a portion of the sleeve is radially in line with at least a portion of the differential bearing when the sleeve is at least one of the first and second sleeve positions such that a plane taken perpendicular to the axis extends through both: the sleeve and the differential bearing.
[0009] [009] Other fields of application will be evident from the description provided here. The description and specific examples in this summary are for the purpose of illustration only and are not intended to limit the scope of this disclosure. BRIEF DESCRIPTION OF THE DRAWINGS
[0010] [010] The drawings described here are for illustrative purposes of selected execution modes only and not for all possible implementations, and are not intended to limit the scope of the present disclosure.
[0011] [011] Figure 1 is a schematic illustration of a vehicle having exemplary sets of axles built in accordance with the teachings of the present disclosure.
[0012] [012] Figure 2 is a bottom perspective view of a portion of the vehicle of Figure 1, illustrating the rear axle assembly in more detail;
[0013] [013] Figure 3 is an exploded bottom perspective view of the rear axle assembly;
[0014] [014] Figure 4 is a sectional view of a portion of the rear axle assembly taken along line 4-4 of Figure 2;
[0015] [015] Figure 5 is an exploded perspective view of a portion of the rear axle assembly illustrating a portion of the differential assembly and the locking mechanism in more detail;
[0016] [016] Figure 6 is a perspective view of a portion of the rear axle assembly illustrating a differential bearing adjuster and an adjusting latch in more detail;
[0017] [017] Figure 7 is a perspective view of the adjusting latch;
[0018] [018] Figure 8 is a sectional view of a portion of the rear axle assembly taken along line 8-8 of Figure 2;
[0019] [019] Figure 9 is a top perspective view of a portion of the rear axle assembly, which illustrates a part of a carrier housing in more detail;
[0020] [020] Figure 10 is a perspective view of a portion of the rear axle assembly, which illustrates a portion of the interior of the carrier housing in more detail; and
[0021] [021] Figure 11 is a perspective view, partially divided in partial view of a lower portion of the rear axle assembly.
[0022] [022] Corresponding reference numbers indicate corresponding parts throughout the various views of the drawings. DETAILED DESCRIPTION
[0023] [023] With reference to Figure 1 of the drawings, an exemplary vehicle 10 is illustrated to include a powertrain 12 and a transmission system 14. The powertrain 12 can include a main engine 20 and a transmission 22. Primary engine 20 it can be an internal combustion engine or an electric motor and can be configured to provide rotary power for the transmission 22. The transmission 22 can be any type of transmission, such as a manual, automatic or continuously variable gearbox, and can be configured to supply rotary power to the transmission system 14.
[0024] [024] The transmission system 14 may include a transfer case 32, a rear transmission shaft 34, the rear axle assembly 36, the front transmission shaft assembly 38 and a transmission shaft assembly 40. The transmission box transfer 32 can receive rotary energy from transmission 22. Rear drive axle 34 can be driven coupled to rear output 42 of gearbox 32 and can transmit rotary energy to rear rear axle assembly 36. Rear axle assembly 36 can be configured to transmit rotary energy to a set of rear wheels of the vehicle 44. The front pivot axle 38 can be driven coupled to a front output 46 of the transfer box 32 and can transmit rotary energy to the front axle assembly 40 The front axle assembly 40 can be configured to transmit rotational energy to a vehicle's front wheel assembly 48. The front and rear axle assembly 1 to 36 and 40 can be constructed according to the teachings of the present revelation. As the front axle assembly 40 is generally similar to that of the rear axle assembly 36, only the rear axle assembly 36 will be discussed in detail here.
[0025] [025] With reference to Figures 2 and 3, the rear axle assembly 36 is shown in more detail. The rear axle assembly 36 may include a housing assembly 50, an input pinion 52, a differential assembly 54, a ring gear 56 and a locking mechanism 58.
[0026] [026] The housing assembly 50 may comprise a carrier housing 60, a pair of shaft tubes 62 and a housing cap 64. The carrier housing 60 may be formed of any suitable material, such as an aluminum alloy material A206 (e.g. 206-T4, T7-206), and you can define a body portion 70 and a pair of tube holders 72.
[0027] [027] With reference to Figures 3 and 4, the body portion 70 can define a cavity 80 that is configured to receive the differential assembly 54 inside it. The body portion 70 may include a pinion support portion 82, a pair of bulkheads 84, a first flange 86 and a locking pair 88. Pinion support portion 82 is configured to receive a pair of pinion bearings 92 that support a shaft portion of the input pinion 52 for rotation about an axis 94 first in relation to the carrier housing 60. Each of the bulkheads 84 can be formed integrally and unitarily with the rest of the carrier housing 60, so that they cannot be removed from the rest of the carrier housing 60. Each of the bulkheads 84 can define a threaded opening 96 that can be arranged around a second axis 98 in a concentric manner with an associated tube mounted 72 The first flange 86 is configured to cooperate with the housing cover 64 to close the cavity 80 and, as such, the first flange 86 can generally extend around the perimeter of the cavity 80. In the example cited, the first flange 86 also extends over lock socket 88. Each lock socket 88 can define a process that can extend through the first flange 86 at a location between one of the associated bulkheads 84 and cavity 80. In the particular example provided, an intermediate wall 100 on the first flange 86 separates each of the locking grooves 88 from the cavity 80, but it will be realized that the recesses defined by the locking groove 88 could intersect the portion of the cavity 80 that is formed through the first flange 86 .
[0028] [028] The assembled tube 72 can be arranged on opposite side sides of the body portion 70 and each of the assembled tubes 72 can be configured to receive an associate of the axle tubes 62, for example in a snap-fit mode. If desired, shaft tubes 62 can be attached to mounted tubes 72 in a way that inhibits axial movement of shaft tubes 62 with respect to mounted tube 72, such as hot weld welding.
[0029] [029] The housing cover 64 can be removably attached to the body portion 70 of the carrier housing 60 to substantially close the cavity 80 that is formed in the housing portion 70. The housing cover 64 can define a second flange 110, a pair of support members 112 and a mounting actuator 114. The second flange 110 can be configured to cooperate with the first flange 86 in the body portion 70 to form a sealing interface. It will be found that a gasket (not specifically shown) or sealing material can be received between the first and second flanges 86 and 110 to form a seal between them. The support members 112 can be molded in any desired shape and can be arranged in line with the locking insert 88 when the box cover 64 is installed in the carrier housing 60. In the example cited, the support members 112 are co-formed with the second flange 110 such that the portions of the inner surface of the housing cover 64 that are defined by the second flange 110 and the support members 112 are coplanar. It will be found, however, that the support members 112 can be of a different shape and that they can extend on one side or the other of the plane that is defined by the inner surface of the second flange 110. The actuator assembly 114 can define a mounting flange 118 that can limit an opening of the actuator 120 that extends through the housing cover 64 and is configured to provide a means for the locking mechanism portion 58 to access the structure that is mounted in the cavity 80. A portion of the locking mechanism 58 can be attached to the housing cover 64 by mounting actuator 114, as will be described in more detail below.
[0030] [030] Differential assembly 54 may include a differential housing assembly 130, a pair of output elements 132 and a power transmission means 134. Output members 132 are rotatably arranged on the second axis 98 and can be directed coupled to the pair of axes (not specifically shown).
[0031] [031] With reference to Figures 4 and 5, the differential case assembly 130 may include a housing body 140 and a cover 142 that can be fixedly coupled to each other by any desired means, including threaded fasteners. In the particular example provided, the cover 142 is welded to the housing body 140. The housing body 140 and the cover 142 can cooperate to define a differential cavity 146 in which the outlet members 132, a portion of the locking mechanism 58, and the energy transmission means 134 can be received. The housing body 140 can include an annular housing wall 148, which is sized to be received through the ring gear 56, and a flange member 150, which can extend radially outwardly from the housing wall 148 The ring gear 56 can be mounted on the flange element 150 in any desired manner, such as by means of a plurality of threaded fasteners or by means of welding, and can be in the form of mesh wrapped with the input pinion 52 ( Fig. 3). In the particular example provided, ring gear 56 and input pinion 52 (Fig. 3) are oriented in carrier housing 60 to form a defined "high compensated" hypoid gear in which the first axis 94 is located vertically above the second axis 98.
[0032] [032] As best shown in Figure 4, the housing body 140 and the cover 142 can define the mounted bearing 160 by a pair of differential bearings 162. In the particular example provided, each of the mounted bearings 160 is formed by recesses that they are formed in the annular wall member 148 and the cap 142. The recesses define an outer annular wall 166 and a shoulder 168. The recesses receive the differential bearings 162 in such a way that the outer raceway of each of the differential bearings 162 is coupled to the outer annular wall 166 and leaning against the shoulder 168 of one of the corresponding recesses. Constructing the differential box assembly 130 in this manner (i.e., with inverted differential bearings) reduces the width of the differential box assembly 130, compared to a conventionally constructed and assembled differential construction process.
[0033] [033] With reference to Figures 3 and 5, the energy transmission means 134 can be any type of device or mechanism for rotary energy transmission between the differential box assembly 130 and the output members 132, and can comprise a or more jaws and / or a differential gear assembly. In the example provided, the power transmission means 134 comprises a differential gear assembly having first and second side helical gears 180 and 182 and a plurality of differential pinion assemblies 184. The first and second side helical gears 180 and 182 can be received in the differential cavity 146 and can be coupled to the output members 132 for common rotation about the second axis 98. The differential gear set can be configured with any number of differential pinion set 184, but in the particular example provided, the set of differential gears include six (6) sets of differential pinions 184. Each set of differential pinions 184 can have a first differential pinion 190, a second differential pinion 192, and a pair of brake shoes 194. The first differential pinions 190 can be received in the first pinion cavity portions 200 of the differential cavity 146 and may have helical teeth that can be engaged with the teeth of the first lateral helical gear 180. The second differential pinions 192 can be received in second portions of pinion cavity 202 of differential cavity 146. Each of the second differential pinions 192 can have helical teeth that can be engaged in gear with the teeth of the second lateral helical gear 182, as well as the corresponding teeth of one of the first differential pinions 190. Each of the brake shoes 194 can be received with an axle end 206 (Fig. 3) one of the correspondents of the first and second differential pinions 190 and 192 and can be received and associated with one of the first and second cavity portions 200 and 202 so as to engage non-rotatively the body of the box 140 or the cover 142 .
[0034] [034] It will be noted that welding the cover 142 to the housing body 140 can produce distortions in the housing body 140 which can impact the coupling of the first and second differential pinions 190 and 192 to the surfaces of the first and second portions of cavity 200 and 202, respectively. In the particular example provided, the weld W (Fig. 4) between the lid 142 and the housing body 140 is displaced axially and radially outwardly from the first and second portions 200 and 202 of the cavity in order to reduce the risk of distortion induced by welding the cover 142 to the housing body 140.
[0035] [035] With reference to Figures 4 and 6, a pair of differential bearing adjusters 210 may be employed to provide bearings 212 on which the differential housing assembly 130 can rotate in relation to the support housing 60, as well as both the preload levels of the differential bearings 162 and to position the differential box assembly 130 in a lateral direction to thereby affect the engagement of ring gear 56 for pinion inlet 52 (Fig. 3). Each of the differential bearing adjusters 210 can define a central opening 220, which can extend longitudinally through the differential bearing adjuster 210, a housing hitch portion 222, a wraparound bearing portion 224, a hitch portion tool 226 and a locking portion 228. The housing engaging portion 222 may comprise an externally threaded segment that can be screwed into the threaded opening 96 in a corresponding bulkhead 84 in the body portion 70 of the carrier housing 60. The engaging portion bearing 224 may comprise bearing 212, which is configured to engage the inner bearing raceway of one of the differential bearings 162, and a shoulder 232 which is configured to abut the inner raceway of the associate of one of the bearings of the differential. differential 162. Tool engagement portion 226 is configured to engage the tool (not shown) to allow a technician to unique to rotate the differential bearing adjuster 210 relative to the carrier housing 60. In the particular example provided, the tool engagement portion 226 comprises a hexagonal opening 236, which coincides with a central opening portion 220 and is configured to engage a tool of correspondingly shaped conduit, and a plurality of holes 238 which can be placed circumferentially over the shoulder 232 radially out of the engagement portion of the housing 222. The prior tool engaging means may be suitable for high volume production before the installation of the shaft assemblies (not shown specifically), while the second means of engagement of the tool may be suitable for repair or service. It will be noted, however, that the redundant coupling tool medium does not need to be provided, and the coupling tool medium provided by the tool engaging portion 226 may be of a different shape. The locking portion 228 may comprise a plurality of locking aspects separated circumferentially by spacing 240 that can be arranged around the circumference of the differential bearing adjuster 210. In the particular example provided, the locking aspects 240 are shaped negatively (i.e., aspects of lock 240 are defined by the material that is removed or is not present in a portion of differential bearing adjuster 210) where each aspect of lock 240 is a groove that extends generally parallel to an axis longitudinal of the differential regulator 210. However, those skilled in the art will note that aspects of lock 240 could be shaped in a positive way (for example, aspects of lock 240 can be defined by a material that is present in a portion of the differential bearing adjuster 210). The locking portion 228 can be located axially along the length of the differential bearing adjuster 210, so as to be positioned in line with one of the locking grooves 88 in the carrier housing 60 when the differential assembly 54 is mounted in the carrier housing 60 and positioned laterally relative to the carrier housing 60 in a desired manner.
[0036] [036] With reference to Figures 4, 6 and 7, a pair of lock adjusters 300 can be used to inhibit the rotation of the differential bearing adjusters 210 in relation to carrier housing 60. Each of the lock adjusters 300 can be formed of a suitable material, such as a plastic or powdered metal material, and may have a locking body 302, a locking profile 304 and a locking flange 306. The locking body 302 is configured to be received sliding into the recess of the corresponding locking insert 88 (Fig. 3), so that the locking adjusters 300 are held in a predetermined position in relation to the carrier housing 60. The locking profile 304 can be configured to engage the bearing adjusters of the differential 210 to inhibit the rotation movement of corresponding one of the bearing adjusters of the differential 210 in relation to the carrier housing 60. The locking profile 304 can comprise locking aspects coupling elements 310 that can fit a part of the locking aspects 240 to the corresponding one of the differential bearing adjusters 210. In the example provided, the locking profile 304 comprises a plurality of spline members that are configured to be received in a subset of locking features 240 which are aligned for locking insert 88. Locking flange 306 can be dimensioned and positioned to contact shoulder 232 of differential bearing adjuster 210, to prevent adjuster locks 300 from being fully inserted in the carrier housing 60, if the differential bearing adjuster 210 is not positioned within predefined limits.
[0037] [037] With additional reference to Figure 8, when the differential bearing adjusters 210 are positioned in order to preload the differential bearings 162 to a desired degree and to position the differential assembly 54 and gear ring 56 laterally on the inside the carrier housing 60, as desired, adjusting latches 300 can be received within locking latch 88 so that the coupling locking aspects 310 on the locking profile 304 can engage in a coupled manner with the locking aspects 240 on the differential bearing adjusters 210. In situations where the differential bearing adjusters 210 are oriented in relation to the carrier housing 60, so that the coupling locking aspects 310 engage the locking aspects 240, the ends outer parts 314 of the adjusting latches 300 can be spaced in a desired way from the contact components 112 by hand than the second flange 110 can be properly positioned in relation to the first flange 86 (i.e., so that the housing cover 64 can be sealed against the carrier housing 60). In practice, a small amount of clearance can be disposed between the outer ends 314 of the adjusting latches 300 and the contact members 112; the clearance, however, is relatively small, so that the adjusting latches 300 cannot move relative to the differential bearing adjusters 210 and the housing cover 64 in an amount that is sufficient to allow aspects of the locking coupling 310 to disengage from locking aspects 240. In situations where differential bearing adjusters 210 are oriented in relation to carrier housing 60, so that coupling locking aspects 310 do not engage locking aspects 240 in a coupled manner. outer ends 314 of the adjusting latches 300 can be spaced from contact members 112 such that the second flange 110 can be improperly positioned in relation to the first flange 86 (that is, so that the housing cover 64 cannot be sealed against the housing carrier 60). The construction in this way allows the adjusting latches 300 to be "dropped into" the carrier housing 60 and eliminates the need for specific installation tools.
[0038] [038] With renewed reference to Figure 3, the height of the carrier housing 60 can be reduced by machining a plurality of surfaces 330 over the interior of the carrier housing 60 to ensure that there is no gap between the carrier housing 60 and the gear ring 56 and that the clearance is smaller in magnitude than would be possible, taking into account stacking tolerances and conventional casting tolerances to control the location of the interior surfaces 330. In the example provided, the clearance between the interior surfaces 330 of the carrier housing 60 and ring gear 56 is less than or equal to 2.0 mm (0.08 inch), preferably less than or equal to 1.5 mm (0.06 inch) and more preferably less than or equal to about 1.0 mm (0.04 inch).
[0039] [039] With reference to Figure 5, the locking mechanism 58 may comprise a first engagement ring 350, a second engagement ring 352, a plunger 354, a locking sleeve or collar 356 and a drive assembly 358. The first and second engagement rings 350 and 352 can generally be similar to the first and second engagement rings described in detail in the generally cited US Patent No. 7,425,185, the disclosure of which is incorporated herein by reference as if they were completely outlined here in detail . Briefly, the first engagement ring 350 may comprise a plurality of first face teeth formed on a surface of the second helical side gear 182 facing the cover 142, while the second engagement ring 352 can be arranged between the first engagement ring 350 and the cap 142 and can have a plurality of second face teeth and a plurality of locking members 360 which can be received in the locking recess 362 which can be formed through the cap 142. The locking members 360 engage the cap 142 so as to slide axially, but non-rotationally coupled to the second engagement ring 352 for the cap 142. It will be noted that the second face tooth coupling for the first face tooth non-rotatively coupled to the second helical side gear 182 for the differential box assembly 130 to thereby block transmission power means 134 and inhibit speed / torque differentiation between output members 132 The plunger 354 can comprise a plurality of legs 370 and a plunger body 372. Each of the legs 370 can be a pin-shaped structure that can be slidably and axially received in one of the locking recesses 362 in the cap 142 and against one of the locking members 360. The plunger body 372 can be attached together with the legs 370 and the second engagement ring 352. In the example provided, the plunger body 372 is formed by a metal ring and a plastic material that the metal ring, legs 370 and locking members 360 over the second engagement ring 352 are supermolded onto it (i.e., cohesively attached to it). Legs 370 can be transported within locking recess 362 to position the second engagement ring 352 in a first position, in which the second face teeth are spaced apart from the first face teeth so that the rotation of the second helical side gear 182 with respect to the cap 142 is not restricted, and a second position in which the second face teeth are coupled to the first face teeth inhibit the rotation of the second helical side gear 182 in relation to the cap 142.
[0040] [040] With reference to Figures 3 and 5, the locking collar 356 can be mounted on the differential case, as for the cover 142, and can be coupled to the differential case for common rotation. In the particular example provided, the locking collar 356 is non-rotatively coupled to the cap 142 and movable axially along the second axis 98, between a first sleeve position and a second sleeve position. In the particular example provided, the cap 142 defines a plurality of longitudinally extending protrusions 380 and the locking collar 356 is coupled contoured so as to slide along the ribs 380, but not to rotate with respect to the cap 142. The locking collar 356 can comprise an engagement surface 384, which can be fixedly coupled with the legs 370 of the plunger 354, and a circumferential groove 386.
[0041] [041] The 358 actuator assembly may be similar to the actuator assembly described in the co-pending application and generally cited Provisional Patent Application No. US61 / 869,282 filed on August 23, 2013, entitled "Power transmission component with actuator in twin-fork ", the disclosure of which is incorporated by reference as being fully known here in detail. Briefly, the actuator assembly 358 can comprise a drive housing 400, a motor 402, a transmission 404, a guide screw (not shown specifically), a support rail 408, a fork rail (not shown specifically), a cradle assembly 412, clutch fork 414, and tension spring (not shown specifically). The actuator housing 400 is configured to at least partially house the remaining components of the 358 drive assembly, and can be mounted on the mounting flange 118 (Fig. 3) of the actuator assembly 114 (Fig. 3) to close the opening of the actuator 120 (Fig. 3). The motor 402 can be an electric motor that can drive the lead screw through the transmission 404. The cradle rail 408 and the fork rail can be fixedly coupled to the housing of the actuator 400 and can generally be arranged parallel to an axis of rotation or longitudinal of the lead screw. The cradle assembly 412 can be threadedly attached to the lead screw and may include a cradle and a compliance spring. The cradle can be slidably mounted on the cradle rail 408 and on the fork rail. The conformity spring can be arranged between the cradle and the lead screw and can be configured to allow axial movement of the conformity spring in relation to the support in at least one direction. The clutch fork 414 can be slidably mounted on the fork rail and can include a pair of arms 420 that can be received in the circumferential groove 386, in the lock collar 356. The bias spring can be discarded on the fork rail between the fork clutch lever 414 and the cradle. The bias spring can skew the clutch fork 414 along the fork rail in a predetermined direction with respect to the cradle assembly 412.
[0042] [042] In operation, motor 402 can be operated to activate the lead screw to cause corresponding movement of the cradle 412 assembly along the fork rail. Moving the cradle assembly 412 in a first direction along the fork rail can cause the clutch fork 414 to move, which can lead to the locking collar 356 (and thus the plunger 354 and the second engagement ring 352) in the direction of the second position of the corresponding sleeve such that the second engagement ring 352 is moved towards its second position. In the event that the movement of the clutch fork 414 in the first direction is interrupted due to tooth-to-tooth contact of the second tooth face with the first tooth face, the bias spring can be compressed to allow the cradle assembly 412 to be positioned and to exert a force on the clutch fork 414 which causes the clutch fork 414 to move in the first direction (to cause directed coupling of the second tooth face with the first tooth face) when the first teeth Tooth faces have been rotatably positioned relative to the second tooth face, in a manner that allows the second engagement ring 352 to fully travel against the first engagement ring 350.
[0043] [043] The movement of the cradle assembly 412 in a second, opposite direction along the fork rail can cause the clutch fork 414 to move, which can lead to the locking collar 356 towards the first position of the sleeve (and thus , the plunger 354 and the corresponding second engagement ring 352) such that the second engagement ring 352 is moved towards its first position. In the event that the clutch fork movement 414 in the second direction is interrupted due to the locking torque of the second tooth face with the first tooth face, the conformity spring can be compressed to allow the cradle to be positioned and to exert a force for clutch fork 414 which makes clutch fork 414 move in the second direction (to cause the second tooth face to disengage from the first tooth face).
[0044] [044] It will be noted that the configuration of the bearing adjusters 210 which is shown here allows the carrier housing 60 to be relatively narrow in width. For example, the locking ring 356 can be arranged concentric on one of the differential bearings 162, so that the rear axle assembly 36 can be provided with locking capabilities without a corresponding need to widen the carrier housing 60. A In this respect, at least a portion of the lock collar 356 may be radially in line with at least a portion of one of the differential bearings 162, when the lock collar 356 is in at least one of the first and second sleeve positions of such so that a plane P taken perpendicular to the second axis 98 extends through both the locking collar 356 and one of the differential bearings 162.
[0045] [045] With renewed reference to Figures 1 and 3, many of the components of the particular rear axle assembly 36 described here and illustrated in the accompanying drawings are configured in such a way that they can also be employed in the front axle assembly 40. Technicians in subject will verify that, because the output members 132 of the differential assembly 54 must rotate in a common direction of rotation, the orientation of the carrier housing 60 must be rotated 180 degrees on (that is, mirrored) the second axis 98 and can optionally be rotated 180 degrees over (i.e., mirrored) the first axis 94. In the particular example provided, the carrier housing 60 is mirrored over both the first and second axis 94 and 98. The configuration in this way guides the input pinion 52 in order to receive the rotating power from the transfer housing 32, as well as causing the input pinion 52 to engage and the ring gear 56 to occur on the opposite side of the first axis 94. The co Configuring in this manner also causes the ring of gears 56 of the rear and front axle assemblies 36 and 40 to rotate in the opposite direction of rotation (relative to the carrier housing 60). This last point is important because the gear ring 56 of the rear axle assembly 36 is used to provide lubrication of the pinion bearings 92 via deep lubrication. Deep lubrication involves the rotation of the gear ring 56 through a reservoir containing the lubricant inside the carrier housing 60 and the subsequent lubricant of the gear ring 56, due to the centrifugal force when the gear ring 56 rotates in a pre-rotation direction -determined (which corresponds to the operation of the vehicle in a predetermined, for example, forward, direction). Typically, the lubricant slag from a gear ring 56 can be driven through lubricant galleries in a desired manner to lubricate several bearings within the rear axle assembly 36. When the direction of rotation of the gear ring 56 relative to the housing carrier 60 is changed, though, the lubricant slag from gear ring 56 will travel in a different direction in relation to carrier 60. Therefore, we have configured carrier 60 with alternative lubrication galleries to provide lubricant for the bearings of the pinion 92, when the carrier housing 60 is oriented differently (for example, mirrored on the first and second axes 94 and 98). Those skilled in the art will notice that, in a situation where the carrier housing 60 is mirrored over the first and second axes 94 and 98, the contact between the input pinion 52 and the gear ring 56 will additionally interfere with the sling. lubrication when the vehicle is operated in the predetermined direction.
[0046] [046] With reference to Figures 9 to 11, the body portion 70 of the carrier housing 60 can define a first lubricant gallery 500 and a second lubricant gallery 502. Optionally, the structure that constitutes the first lubricant gallery 500 and / or the structure that constitutes the second lubricant gallery 502 can be used to reinforce the portions of the carrier housing 60. In the particular example provided, the structures that form the first and second galleries lubricant 500 and 502 form ribs on the outside of the remainder of the carrier housing 60 that reinforce the portions of the desired carrier housing 60. For example, the structure that constitutes the second lubricant gallery 502 is configured to support the portion of the carrier housing 60 that is loaded by the input pinion 50 during operation of the axle assembly when the vehicle is used in a predetermined (for example, forward) direction.
[0047] [047] The first lubricant gallery 500 can define a channel that extends between the cavity 80 and the portion of the carrier housing 60 on which the pinion bearings 92 (Fig. 2) are mounted. The end of the first lubricant gallery 500, which intersects the cavity 80, can be oriented to receive the lubricant that is dripping from the gear ring 56 (Fig. 3) when the carrier housing 60 is used for mounting the rear axle 36 (Fig. 1) and vehicle 10 (Fig. 1) is driven in a forward direction. Accordingly, the end of the first lubricant gallery 500 of interest to the cavity 80 can be oriented vertically above the second axis 98 (Fig. 5). The first gallery of lubricant 500 can be tilted so that it falls vertically with a reduction in the distance to the pinion bearings 92 (Fig. 3) when the carrier housing 60 is oriented for use in the assembly of the rear axle 36 (Fig. 1 ). The configuration in this way allows the gallery of the first lubricant 500 to be used to feed (by gravity) lubricant from the cavity 80 to the pinion bearings 92 (Fig. 3) when the carrier housing 60 is oriented for use when mounting the rear axle 36 (Fig. 1). When the carrier housing 60 is mirrored on the first and second axes 94 and 98 for use on the front axle assembly 40 (Fig. 1), the first lubricant gallery 500 is configured to drain excess lubricant with the pinion bearings 92 (Fig. 3) for cavity 80.
[0048] [048] The second lubricating gallery 502 can define a channel that extends between the cavity 80 and the portion of the carrier housing 60 to which the pinion bearings 92 (Fig. 2) are mounted. The end of the second lubricant gallery 502, which intersects the cavity 80, can be oriented to receive the lubricant which is launched from the inlet portion of the pinion gear 52 (Fig. 3) when the carrier housing 60 is used for assembly from the front axle 40 (Fig. 1) and vehicle 10 (Fig. 1) is driven in a forward direction. Therefore, the end of the second lubricant gallery 502 that intersects the cavity 80 can be oriented vertically below the end of the first lubricant gallery 500, which intersects the cavity 80 and on one side of the first axis 94 which is opposite the end of the first lubricant gallery 500 that intersects the cavity 80. When the carrier housing 60 is oriented for use in the assembly of the rear axle 36 (Fig. 1), the gallery of the second lubricant 502 can be configured to drain the excess lubricant from the gallery of the first lubricant 500 and, in addition, it can be positioned to drain the lubricant to part of the pinion inlet gear 52. When the carrier housing 60 is oriented for use in the assembly of the front axle 40 (Fig. 1), the lubricant can be drained from the inlet portion of the pinion gear 52 and can be received inside the gallery end of the second lubricant and 502, which intersects cavity 80; the excess lubricant can drain into cavity 80 through the open end of the gallery of the first lubricant 500.
[0049] [049] The previous description of the execution modes has been provided for purposes of illustration and description. It is not intended to be exhaustive or to limit disclosure. Individual elements or aspects of a particular embodiment are generally not limited to that particular embodiment, but, where applicable, are interchangeable and can be used in a selected embodiment, even if it is not specifically shown or described. It can also be varied in many ways. Such variations should not be seen as a departure from the description, and all such changes are intended to be included within the scope of the disclosure.

权利要求:
Claims (19)
[0001]
An axis assembly (36) characterized by comprising: a locking differential assembly (54) having a differential housing (130), a ring gear (56) coupled to the differential housing (130) for rotation, first and second output members (132), and a locking element ( 352), which moves mounted to the differential box (130); an axle housing (50) having a center section (60) that defines a pinion mounting portion (82), a cavity (80), an opening and a first flange (86) that borders the opening, the dimensioned opening to receive the locking differential assembly (54), the locking differential assembly (54) received in the cavity (80) for rotation about an axis (98), the ring gear (56) extending through the opening, the first flange (98) defining a sealing surface parallel to, and offset from, the axis (98); an input pinion (52) received at the pinion mounting portion (82), the input pinion (52) having a rod and pinion, the pinion being disposed in the cavity (80); a pair of pinion bearings (92) received at the pinion mounting portion (82) and which support the rod for rotation in relation to the center section (60); a cover (64) mounted on the first flange (86) in the central section to partially close an open side of the cavity (80), the cover (64) defining a drive opening (120) that allows access through the cover (64) to the cavity (80); and a drive assembly (58) comprising a sleeve (356) and an actuator (358), the sleeve (356) being mounted on the differential case (130) and movable along the axis (98) between a first position of sleeve and a second position sleeve, the actuator (358) is mounted on the outer side of the cover (64) and extends through the opening of the actuator (120) to engage the sleeve (356), the actuator (358) it is configured to selectively move the sleeve (356) between the first and second sleeve positions, where the locking differential assembly (54) is configured to operate in an unlocked mode that allows the speed differentiation between the first and second elements of output (132) when the sleeve (356) is in the first sleeve position, and in which the locking differential assembly (54) is configured to be operated in a locked mode, which inhibits the speed differentiation between the first and second members of outlet (132) when the sleeve (356) is in the second position of the hand ga.
[0002]
The shaft assembly (36) of claim 01, characterized in that the actuator (358) comprises a fork (414) that engages the sleeve (356).
[0003]
The shaft assembly (36) of claim 01, characterized in that the sleeve (356) is joined to the differential housing (130) for common rotation.
[0004]
The shaft assembly (36) of claim 01, characterized in that the locking differential assembly (54) is supported for rotation with respect to the central section (60) of the shaft housing (50) by a pair of differential bearings (162) and wherein at least a portion of the sleeve (356) is radially in line with at least a portion of one of the differential bearings (162) when the sleeve (356) is in the first position of the sleeve.
[0005]
The axle assembly (36) of claim 04, characterized in that the differential case (130) defines a bearing bore (160) and in which one of the bearing differentials (162) comprises an outer raceway which is received at the bearing bore (160) and engaged in the differential case (130).
[0006]
The shaft assembly (36) of claim 05, characterized in that a radially inner side of one of the differential bearings (162) is supported on a bearing adjuster (210) which is movably mounted to the central section (60) of the housing of the axis (50).
[0007]
The shaft assembly (36) of claim 06, characterized in that the bearing adjuster (210) is threadedly connected to the central section (60).
[0008]
The shaft assembly (36) of claim 01, characterized in that each of the first and second outlet elements (132) is coupled to a side gear (180, 182) for common rotation.
[0009]
The shaft assembly (36) of claim 01, characterized in that the locking differential assembly (54) comprises a defined differential gear that has a pair of side gears (180, 182) and a plurality of differential pinions (190, 192) .
[0010]
The shaft assembly of claim 09, characterized in that the differential gear assembly is a helical gear assembly.
[0011]
An axis assembly (36) characterized by comprising: an axle housing (50) having a central section (60) defining a cavity (80); a blocking differential assembly (54) received in the cavity (80), the blocking differential assembly (54) having a differential box (130), first and second output elements (132), and a blocking element ( 352) which is movably mounted to the differential case (130), the differential case (130) defining a bearing bore (160); a differential bearing (162) having an outer race bearing, the outer bearing raceway received in the bearing bore (160) and wrapped with the differential housing (130), the bearing differential (162) that supports one end of the assembly locking differential (54) for rotation about an axis (98) in relation to the shaft housing (50), the bearing differential (162) having a directed preload pressure between the shaft housing (50) and the differential box (130) in a predetermined direction along the axis (98); and an actuator assembly (58) having a sleeve (356) and an actuator (358), the sleeve (356) being mounted on the differential case (130) and movable along the shaft (98) between a first sleeve position and a second sleeve position, the actuator (358) being coupled to the shaft and sleeve housing (50), the actuator (358) being configured to selectively move the sleeve (356) between the first and second sleeve positions, wherein the locking differential assembly (54) is configured to operate in an unlocked mode that allows speed differentiation between the first and second output elements (132) when the sleeve (356) is in the first position of the sleeve, where the locking differential assembly (54) is configured to operate in a locking mode that inhibits speed differentiation between the first and second output members (132) when the sleeve (356) is in the second position of the sleeve and in which at least least one portion of the sleeve (356) is radially in line with at least a portion of the differential bearing (162) when the sleeve (356) is in at least one of the first and second sleeve positions such that a plane (P) of a plane perpendicular to the axis (98) extends through both the sleeve (356) and the differential bearing (162).
[0012]
The shaft assembly (36) of claim 11, characterized in that the actuator (358) comprises a fork (414) that engages the sleeve (356).
[0013]
The shaft assembly (36) of claim 11, characterized in that the sleeve (356) is joined to the differential housing (130) for common rotation.
[0014]
The axle assembly (36) of claim 11, characterized in that a plurality of legs are mounted on the locking element (352), the legs (370) extending through the differential case (130) and being arranged in a transmission path of force in which the force is transmitted between the sleeve (356) and the locking element (352).
[0015]
The shaft assembly (36) of claim 11, characterized in that a radially internal side of the differential bearing (162) is supported on a bearing adjuster (210) which is movably mounted to the central section (60) of the shaft housing ( 50).
[0016]
The shaft assembly (36) of claim 15, characterized in that the bearing adjuster (210) is threadedly connected to the central section (60).
[0017]
The shaft assembly (36) of claim 11, characterized in that each of the first and second outlet elements (132) is coupled to a side gear (180, 182) for common rotation.
[0018]
The shaft assembly (36) of claim 11, characterized in that the locking differential assembly (54) comprises a defined differential gear that has a pair of side gears (180, 182) and a plurality of differential pinions (190, 182) .
[0019]
The shaft assembly (36) of claim 18, characterized in that the differential gear assembly is a helical gear assembly.

类似技术:

公开号 | 公开日 | 专利标题

BR102015008968B1|2021-02-17|compact shaft assembly with locking differential

US9157515B2|2015-10-13|Axle assembly

US20090011890A1|2009-01-08|Locking differential including disengagement retaining means

JP2011162179A|2011-08-25|Power transmission system

BRPI1100128B1|2020-02-04|vehicle differential gear

US9726227B2|2017-08-08|Final drive disconnect mechanism

BR102016017942A2|2018-02-27|SHAFT ASSEMBLY WITH CLUTCH BEARING ACTUATOR MECHANISM

BR102016009392B1|2021-04-27|AXLE ASSEMBLY HAVING A BARRIER MODULE

CN108351021B|2021-05-04|Lubricant flow regulating system and axle assembly made therewith

BR112012016525B1|2021-06-22|CRUSHER

JP2005207578A|2005-08-04|Torque transmission device

KR101764028B1|2017-08-01|Apparatus for adjusting back lash of gear for transfer

JP6154639B2|2017-06-28|transmission

ES2812803T3|2021-03-18|Transmission

US11235654B2|2022-02-01|Axle assembly

BR102019028011A2|2020-10-20|PLANETARY GEAR TRAIN.

CA2898974C|2019-05-14|Final drive disconnect mechanism

BR102017008655A2|2018-02-06|DRIVE SET

WO2017170526A1|2017-10-05|Drive device and production method for drive device

BRPI1001493B1|2020-05-26|ROTARY AXLE SUPPORT BOX STRUCTURE

JP2008286317A|2008-11-27|Driving force distribution transmission

JP2014134229A|2014-07-24|Viscous coupling

同族专利:

公开号 | 公开日

BR102015008968A2|2015-12-15|

BR102015008978A2|2016-11-01|

CN109944917A|2019-06-28|

CN105020360A|2015-11-04|

DE102015105956A1|2015-10-29|

KR20150122599A|2015-11-02|

KR102175358B1|2020-11-06|

US9074678B1|2015-07-07|

US9022892B1|2015-05-05|

CN105020363A|2015-11-04|

US9259967B2|2016-02-16|

US9140349B1|2015-09-22|

DE102015105958A1|2015-10-29|

CN105020363B|2019-04-09|

US20150306909A1|2015-10-29|

CN105020360B|2018-04-27|

CN105020360B8|2018-09-28|

引用文献:

公开号 | 申请日 | 公开日 | 申请人 | 专利标题

US1786492A|1929-12-19|1930-12-30|Jacob T Hustvet|Differential clutch|

US1888884A|1931-11-12|1932-11-22|Harry F Omer|Drive axle gearing|

US2061009A|1934-11-24|1936-11-17|Gen Motors Corp|Rear axle construction|

US2152771A|1936-03-16|1939-04-04|Clark Equipment Co|Two-speed rear axle|

US2742684A|1952-09-23|1956-04-24|Bill W Rising|Power divider|

US3318173A|1965-03-19|1967-05-09|American Motors Corp|Differential gear assembly|

FR1539811A|1967-07-25|1968-09-20|Herwaythorn Sa|Motor vehicle drive axle|

US4043224A|1974-06-12|1977-08-23|Allis-Chalmers Corporation|Mechanical differential lock|

US5269731A|1991-10-30|1993-12-14|Dana Corporation|Differential unit having adjustable bearing assemblies|

ZA949349B|1993-11-29|1995-07-25|Gearmax Proprietary Limited|Drive axle for a motor vehicle|

US5540300A|1995-01-09|1996-07-30|American Axle & Manufacturing Inc.|Drive axle assembly with lubricant cooling system|

US5711738A|1995-07-24|1998-01-27|Nsk Ltd.|Conical roller bearing for supporting a pinion shaft of differential gear|

US5839327A|1995-09-18|1998-11-24|American Axle & Manufacturing, Inc.|Drive axle assembly with lubricant cooling system|

US5806371A|1996-07-23|1998-09-15|American Axle & Manufacturing, Inc.|Gear arrangement with backlash adjustment|

US6155135A|1998-11-23|2000-12-05|American Axle & Manufacturing, Inc.|Drive unit with lubricant cooling cover|

US6227716B1|1999-08-20|2001-05-08|Earl J. Irwin|Differential unit having an adjustable bearing assembly|

US6398689B1|2000-03-27|2002-06-04|American Axle & Manufacturing, Inc.|One piece differential bearing adjuster lock and fastener|

US6532660B1|2000-09-14|2003-03-18|Torque-Traction Technologies, Inc.|Backlash adjuster with bevel gear face for adjustment with mating geared tool|

US20030099670A1|2001-02-09|2003-05-29|Gert Hobom|Influenza viruses with enhanced transcriptional and replicational capacities|

JP4552341B2|2001-03-26|2010-09-29|アイシン精機株式会社|Differential equipment for four-wheel drive vehicles|

US20030096670A1|2001-11-16|2003-05-22|Spicer Technology, Inc|Differential transmission apparatus|

JP2003166624A|2001-11-28|2003-06-13|Toyota Motor Corp|Support structure for rotary shaft|

KR100617464B1|2002-08-06|2006-09-01|도치기 후지 산교 가부시키가이샤|Actuator and intermissive power transmission device therewith|

CN2554037Y|2002-07-03|2003-06-04|东风农机集团公司|Front driving axle differential bearing adjusting device of wheel tractor|

US6958030B2|2003-09-29|2005-10-25|American Axle & Manufacturing, Inc.|Electromagnetic locking differential assembly|

US7585032B2|2003-10-17|2009-09-08|American Axle & Manufacturing, Inc.|Modular axle assembly|

US20060276298A1|2003-11-26|2006-12-07|Rodgers Mark E|Bearing adjuster lock and method of use|

GB0404547D0|2004-02-28|2004-03-31|Mason Kevin A|Differential locking system|

US7022041B2|2004-03-05|2006-04-04|American Axle & Manufacturing, Inc.|Helical gear differential|

US7108428B2|2004-10-19|2006-09-19|American Axle & Manufacturing, Inc.|Axle assembly with bearing adjustment mechanism|

US7175560B2|2005-01-20|2007-02-13|American Axle & Manufacturing, Inc.|Thermally compensating bearing preload arrangement in axle assembly|

US7211020B2|2005-05-26|2007-05-01|American Axle & Manufacturing, Inc.|Lockable differential with locking state detection system|

CN1975210A|2005-10-19|2007-06-06|达纳公司|Axle assembly bearing positioning and preload adjustment tool and method of implementing same|

US7602271B2|2006-08-21|2009-10-13|American Axle & Manufacturing, Inc.|Electronically actuated apparatus using solenoid actuator with integrated sensor|

US7572202B2|2007-01-31|2009-08-11|American Axle & Manufacturing, Inc.|Electronic locking differential with direct locking state detection system|

US8109000B2|2007-05-31|2012-02-07|American Axle & Manufacturing, Inc.|Salisbury axle assembly|

US7837588B2|2007-07-20|2010-11-23|American Axle & Manufacturing, Inc.|Pre-load mechanism for helical gear differential|

US8070641B2|2007-08-14|2011-12-06|Autotech Sport Tuning Corporation|Differential gear assembly|

US7775928B2|2007-09-21|2010-08-17|American Axle & Manufacturing, Inc.|Differential and bearing arrangement|

US20090082126A1|2007-09-24|2009-03-26|Harrison Robert S|Putter club holder|

US7794153B2|2007-12-07|2010-09-14|Ford Global Technologies, Llc|Adjusting and maintaining bearing preload in an axle assembly|

CN101354232B|2008-06-25|2010-10-13|辽宁曙光汽车集团股份有限公司|Method and system for measuring and choosing adjusting washer of differential bearing of cannula type main gearbox assembly|

US8109174B2|2008-08-22|2012-02-07|American Axle & Manufacturing, Inc.|Differential cover providing lubricant flow control|

US8409044B2|2008-10-23|2013-04-02|American Axle & Manufacturing, Inc.|Differential lubrication feed system in a drive axle assembly|

US8167758B2|2008-12-08|2012-05-01|American Axle & Manufacturing, Inc.|Drive axle assembly with gear mesh lubrication systems for lubricating gear mesh and/or differential bearings|

US8167762B2|2009-04-24|2012-05-01|American Axle & Manufacturing, Inc.|Drive axle assembly with wheel speed measurement system|

US8152672B2|2009-07-24|2012-04-10|Honda Motor Company, Ltd.|Differential assembly including differential lock and blocking member|

US8475314B2|2010-01-28|2013-07-02|American Axle & Manufacturing, Inc.|Differential assembly with features for improved lubrication|

US20110269595A1|2010-04-30|2011-11-03|American Axle & Manufacturing Inc.|Control strategy for operating a locking differential|

CN201858337U|2010-11-09|2011-06-08|中国第一汽车集团公司|Internally-locking type adjusting ring of differential bearing of automobile drive axle|

CN102478109A|2010-11-29|2012-05-30|张惠杰|Mechanical lock-type differential|

US20120283060A1|2011-05-02|2012-11-08|American Axle & Manufacturing, Inc.|Lubrication distribution within rear drive module|

US8475320B2|2011-05-19|2013-07-02|American Axle & Manufacturing, Inc.|Bearing preload adjuster|

CN202056209U|2011-05-20|2011-11-30|徐工集团工程机械股份有限公司科技分公司|Adjustment structure for tapered roller bearings|

CN202531772U|2012-01-10|2012-11-14|邱杰|Taper key sleeve type self-locking differential|

CN104379970B|2012-04-19|2017-12-15|舍弗勒技术股份两合公司|Planetary gear mechanism|

US8657716B1|2012-09-13|2014-02-25|American Axle & Manufacturing, Inc.|Drive train component with structural cover|

US8534925B1|2012-09-21|2013-09-17|American Axle & Manufacturing, Inc.|Differential bearing system for an axle assembly|

JP6212862B2|2012-12-27|2017-10-18|株式会社ジェイテクト|Liquid lubricated bearing and vehicle pinion shaft support device|

US8460149B1|2013-01-25|2013-06-11|American Axle & Manufacturing, Inc.|Differential bearing system for a power transmitting component and method for assembling a power transmitting component|

US9103430B2|2013-03-14|2015-08-11|American Axle & Manufacturing, Inc.|Power transmitting component with a differential bearing system|

CN203500446U|2013-09-23|2014-03-26|芜湖世特瑞转向系统有限公司|Clearance adjusting and locking mechanism for gear and rack hydraulic steering machine|

CN103697140A|2013-11-29|2014-04-02|浙江吉利控股集团有限公司|Adjuster for conical bearing of differential|ES2589464T3|2011-06-24|2016-11-14|Mitsubishi Electric Corporation|Gear unit|

US9517658B2|2014-07-11|2016-12-13|American Axle & Manufacturing, Inc.|Axle assembly with carrier housing having increased strength and reduced mass|

US9919559B2|2014-12-11|2018-03-20|Ford Global Technologies, Llc|Axle carrier housing with a swept support rib|

US9989139B2|2015-06-18|2018-06-05|Arvinmeritor Technology, Llc|Axle assembly having a clutch collar actuator|

US10871218B2|2015-07-28|2020-12-22|Magna Powertrain Of America, Inc.|Injection molded retention method for power transfer devices|

US9651131B2|2015-09-11|2017-05-16|American Axle & Manufacturing, Inc.|Clutch system configured to enhance engagement performance of clutch teeth|

US10267401B2|2015-11-25|2019-04-23|American Axle & Manufacturing, Inc.|Axle assembly|

WO2017106095A1|2015-12-15|2017-06-22|American Axle & Manufacturing, Inc.|Axle assembly|

US10132400B2|2016-01-19|2018-11-20|Ford Global Technologies, Llc|Differential mounting system|

CN109073060A|2016-06-01|2018-12-21|吉凯恩传动系统日本株式会社|Spiral LSD lid with clutch|

JP6457476B2|2016-12-20|2019-01-23|本田技研工業株式会社|Power equipment|

US10710406B1|2016-12-20|2020-07-14|Volvo Truck Corporation|Assembly for a vehicle axle including a differential|

JP6518718B2|2017-05-09|2019-05-22|本田技研工業株式会社|Power plant|

CN107355525A|2017-06-12|2017-11-17|湖北航天技术研究院特种车辆技术中心|A kind of differential mechanism|

US10670129B2|2017-11-17|2020-06-02|American Axle & Manufacturing, Inc.|Clutched component|

CN108944270B|2018-08-03|2021-08-10|安徽天裕汽车零部件制造有限公司|Automobile rear axle|

CN111219447A|2020-03-17|2020-06-02|苏州大学|Cambered surface secondary envelope crown gear nutation transmission device|

法律状态:
2015-12-15| B03A| Publication of an application: publication of a patent application or of a certificate of addition of invention|

2018-10-30| B06F| Objections, documents and/or translations needed after an examination request according art. 34 industrial property law|

2020-04-07| B06U| Preliminary requirement: requests with searches performed by other patent offices: suspension of the patent application procedure|

2020-12-08| B09A| Decision: intention to grant|

2021-02-17| B16A| Patent or certificate of addition of invention granted|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 20/04/2015, OBSERVADAS AS CONDICOES LEGAIS. |

优先权:

申请号 | 申请日 | 专利标题

US201461983092P| true| 2014-04-23|2014-04-23|

US61/983,092|2014-04-23|

US14/529,449|US9140349B1|2014-04-23|2014-10-31|Compact axle assembly with locking differential|

US14/529,449|2014-10-31|

[返回顶部]