Patent Publication Number: US-2015087461-A1

Title: Banjo Type Rear Axle Assembly with Drop Out Third Member

Description:
CROSS-REFERENCES TO RELATED APPLICATIONS 
     This application claims the benefit of U.S. Provisional Application 61/704,301 No. filed Sep. 21, 2012. 
     FIELD OF ART 
     This invention relates to rear drive axles and drop out third member carriers in banjo type axle assemblies. 
    
    
     BACKGROUND 
     Rear drive axle assemblies with differentials are well known in the art of motor vehicles. The concept of bifurcating power from a single input into two different power outputs with the potential of having unequal power distribution between the outputs has been known in the art since the development of bevel gears and pinions by Onesiphore Pecqueur in 1827. Since the development of bevel gear sets, this art has been applied in an array of different motor vehicles and currently underlines the mechanical basis for distributing power for many rear axle assembly units. The common elements in the art of rear axle assemblies are the following: the drive pinion assembly, the ring gear assembly, the rotatable differential house assembly with a differential bevel and pinion gear set, the axle housing, the differential bearing clamp assembly, and the rear axle shafts. 
     In a common rear axle assembly, the drive pinion assembly communicates with the drive shaft assembly via a universal joint and transmits torque from the drive shaft assembly to the ring gear assembly. The drive pinion assembly articulates directly with the ring gear assembly as a spiral bevel gear set where the teeth from the pinion shaft assembly articulates with the teeth from the ring gear assembly. The pinion shaft transmits longitudinal torque, which rotates around the axis running between the front of the vehicle to the rear of the vehicle, to the ring gear set which translates the longitudinal torque into lateral torque, which rotates around the axis running between side one and side two of the vehicle. 
     In addition to translating longitudinal torque into lateral torque, the articulation between said teeth of the drive pinion assembly and said teeth from the ring gear assembly functions to create a ratio between the number of rotations of said pinion shaft assembly during period of time X per the number of rotations of said ring gear assembly during period of time X. This ratio in rotational rates is created because the ring gear assembly often has more teeth than the pinion shaft assembly, and as a consequence the pinion shaft assembly completes an entire rotation faster than the ring gear assembly completes an entire rotation. Some common ratios in rotational rates in the art between the pinion gear shaft assembly and ring gear assembly are: 3.21:1, 3.42:1, 3.73:1, 4.10:1, 4.56:1, 4.88:1, 5.13:1, and 5.38:1. 
     This ratio in rotational rates between the pinion shaft assembly and the ring gear assembly influences a vehicle&#39;s gas mileage, toque, acceleration, top velocity, and ability to climb hills. Where the ratio is greater between the pinion gear rotation per time and the ring gear assembly rotation per time (e.g. 5.38:1), there is an increase in the torque of the ring gear assembly per the input of the toque of the pinion shaft assembly, but inversely a reduction in the radians per second of the ring gear assembly per the radians per second of the pinion shaft assembly. This is based on basic principles involving lever arms where increases in length of the radius from the axis of rotation correlate with increases in torque. The increase of the torque of the ring gear assembly per input of torque of the pinion shaft assembly is associated with increases in vehicle&#39;s towing ability, initial acceleration, and hill climbing. However increases of the torque of the ring gear assembly per input of torque of the pinion shaft is associated with decreases in vehicle&#39;s gas mileage and top velocity as a consequence of the decrease of radians per second of the ring gear assembly. 
     While often correlated with the number of teeth of ring gear assemblies in the art, the diameter of the ring gear also influences the strength of the ring gear assembly and as a consequence the failure rate of the rear gear assembly. This correlation between diameter and strength results from being able to make the teeth wider in a ring gear with a larger diameter. Common ring gear assemblies range in diameters from 7.25 in. to 10.5 in. 
     The ring gear assembly is affixed to the differential house assembly, and as the ring gear rotates with said lateral torque, the differential house rotates accordingly. Within said differential house, the differential pinion and bevel gear set bifurcates the lateral torque from the ring gear into the first rear axle shaft and the second rear axle shaft. Said rear axle shafts communicate the divided lateral torque into first tire assembly and second tire assembly. The divided lateral torques in said first and second axle shafts can be substantially similar when the vehicle is driving in a substantially straight path and can be different where one of said axle shafts rotates faster than the other of said axle shafts sufficient when the vehicle is driving around a corner one of the said tire assemblies on the outside of the corner rotates faster than the other of the said tire assemblies on the inside of the corner. 
     Another factor that influences the bifurcation of said lateral torque within said differential house is the relative traction experienced between said first tire assembly and said second tire assembly. When said first tire assembly or alternatively said second tire assembly experiences less traction than the alternative tire assembly, then it will spin faster than the alternative tire assembly unless there is a means to lock said differential house to bifurcate the lateral torque substantially equally between said tire assemblies except when the vehicle drives around a corner. In the art, there are several mechanisms to lock said differential house or to compensate for differences in lateral torque resulting from differences in traction. These mechanisms include the following: limited-slip differentials, traction control systems, automatic differential lockers, selective differential lockers, and spools. 
     The axle housing can either be unitized such as in a Salisbury type axle assembly or have a drop out third member carrier such as in a Banjo type axle assembly. In a Salisbury type axle assembly, the pinion shaft assembly, the ring gear assembly, the rotatable differential house assembly and the ring gear clamp assembly are accessible through an aperture with a cover in the rear of the axle housing. The cover is affixed to the rest of the axle housing by bolts. While a Salisbury type axle assembly is more common than a Banjo type axle assembly, there are some disadvantages to this type of axle assembly. Because the axle housing is unitized, there is no easy mechanism to change the differential bevel gear set or ring gear assembly. To change the inner components of the Salisbury axle, one can either work underneath a vehicle or entirely remove the rear axle and brake assembly from the vehicle&#39;s chassis. This inhibits the ability of vehicle enthusiasts to access and replace easily differential houses and other components in the axle housing with replacement parts and after-market parts. 
     The Banjo type axle assembly has a drop out third member carrier for the pinion shaft assembly, ring gear assembly, the rotatable differential house assembly with a differential bevel and pinion gear set, and the ring gear clamp assembly. Commonly in the art, the drop out third member carrier is affixed to the rear axle housing with bolts. The pinion shaft is adjusted to engage teeth of the ring gear assembly with shims. Unlike the Salisbury axle, one can remove the drop out third member carrier to change or work on the inner components of the rear axle without having to remove the entire rear axle and brake assembly from the vehicle&#39;s chassis. The relative ease of removing the drop out third member carrier provides an advantage for competitive racers and recreational users who want to be able to adjust their rear axle&#39;s components to achieve optimal rotational ratios between the pinion shaft assembly and the ring gear assembly. It also allows vehicle enthusiasts the ability to install custom of after-market features to their rear gears including differential lock mechanisms. However, Banjo type axles in the art are not designed for 10.5 in diameter ring gears which impart strength and the ability of having higher lateral torque per input of longitudinal torque. 
     Regardless of whether an rear axle has a Banjo type axle assembly or a Salisbury type axle assembly, rear axles are known to fail while being driven over rough terrain. With the heightened popularity of off-road racing and recreational off-road driving, there is a need for a rear axle to be designed to be durable enough to not fail irrespective of the terrain. There is also the need for rear axle assemblies to have the capacity to have high lateral torque relative to the input of longitudinal torque so that vehicles with said rear axle assemblies can have increased initial acceleration, climbing power and towing capacity. There is a need for a rear axle to provide adequate clearance underneath a vehicle so that the vehicle does not get stuck while climbing over rough terrain. There is a need for a rear axle assembly where components can be easily repaired and after-market replacement parts can be easily installed so that racers and off-roading enthusiasts can easily repair broken rear axles in rough terrain and can achieve competitive advantages with specialized after-market parts. 
     Information associated with rear axle assemblies can be located in the following references: US832991, U.S. Pat. No. 1,950,034, U.S. Pat. No. 1,955,824, U.S. Pat. No. 1,973,905, U.S. Pat. Nos. 2,124,406, 2153287, U.S. Pat. No. 2,188,316, U.S. Pat. No. 2,561,335, U.S. Pat. No. 2,817,251, U.S. Pat. No. 3,270,583, U.S. Pat. No. 3,930,421 A, U.S. Pat. No. 4,004,472 A, U.S. Pat. No. 4,018,097 A, U.S. Pat. No. 4,221,138 A, U.S. Pat. No. 4,625,581 A, U.S. Pat. No. 4,787,267 A, U.S. Pat. No. 5,442,977 A, U.S. Pat. No. 5,480,360 A, U.S. Pat. No. 5,533,423 A, U.S. Pat. No. 5,584,777 A, U.S. Pat. No. 5,733,216 A, U.S. Pat. No. 5,938,558 A, U.S. Pat. No. 5,951,431 A, U.S. Pat. No. 6,176,152 B1, U.S. Pat. No. 6,436,002 B1, U.S. Pat. No. 6,595,085 B1, U.S. Pat. No. 6,645,113 B2, U.S. Pat. No. 6,743,136 B1, U.S. Pat. No. 6,976,929 B1, U.S. Pat. No. 7,004,277 B2, U.S. Pat. No. 7,223,192 B2, U.S. Pat. No. 7,320,659 B2, U.S. Pat. No. 7,827,882 B2, U.S. Pat. No. 7,866,433 B2, U.S. Pat. No. 8,152,680 B2, US832991, U.S. Pat. No. 8,371,415 B2, US20120316024 A1, EP1717486 A2, EP2446172 B1. 
     However, each of these references has one or more of the following deficiencies: references with Banjo type rear axles may not have enough space to house larger diameter ring gears which are associated with greater strength and higher ratio&#39;s between the radians per second of ring gear assembly and radians per second of the pinion shaft assembly; references with Salisbury axles do not allow for ease of accessing and replacing the differential housing; many references are not adequately designed for off-road conditions with sufficient clearance under the vehicle and structural materials; and many references are not designed for after-market parts or access ports for specialized features. 
     SUMMARY 
     The present invention is directed to a Banjo type axle assembly with a drop out third member carrier for the pinion shaft assembly, ring gear assembly, the rotatable differential house assembly and the differential bearing clamp assembly. Said drop out third member carrier and the rear axle housing are constructed sufficiently to house a 10.5 inch diameter ring gear. In one preferred embodiment the drive pinion assembly and the ring gear assembly exhibit a mild hypoid gear set orientation. In one preferred embodiment said drop out third member carrier has substantially uniform dimensions in thickness and has a symmetrical bolt pattern between a pinion shaft side and a non-pinion shaft side with a total of twelve bolts to affix said drop out third member to carrier to said rear axle housing. An oiling shelf has extra material to house pinion bolts as part of the pinion shaft assembly. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       These and other features, aspects, and advantages of the present invention will become better understood with regard to the following description, appended claims and accompanying drawings where: 
         FIG. 1  shows an anterior view of the rear axle assembly with the drop out third member carrier assembly and the body and shafts of the axle housing; 
         FIG. 2  shows an exploded view the rear axle assembly with the drop out third member carrier assembly, the drive pinion assembly and the body and shafts of the axle housing; 
         FIG. 3  shows a side view of the drop out third member carrier assembly with the rotatable differential house assembly; 
         FIG. 4  shows an anterior view of the drop out third member carrier assembly; 
         FIG. 5  shows a side view of the drop out third member carrier assembly without the rotatable differential house assembly; and 
         FIG. 6  shows a posterior side of the drop out third member carrier assembly. 
     
    
    
     DESCRIPTION 
     This description first defines the components of the present invention and then describes in the same order the preferred embodiments of said components. 
     DEFINITIONS 
     1. “Drop out Third Member Carrier Assembly”  1 —is a carrier apparatus with the fasteners necessary to affix to the axle housing and carries the drive pinion assembly  11 , the ring gear assembly  16 , the rotatable differential house assembly  17  with the differential bevel and pinion gear set, and the differential bearing clamp assembly  19 . 
     2. “Drive Pinion Assembly”  11 —is the drive pinion, pinion teeth, cups, bearings, shims, nuts, seals, and spacers necessary to translate longitudinal torque from the universal joint to the ring gear assembly  16  while traveling through an aperture in the drop out third member carrier assembly  10 . 
     3. “Ring Gear Assembly”  16 —is the ring gear with its teeth and fasteners necessary to articulate with the pinion teeth and affix to the rotatable differential house assembly  17 ; it functions to translate and transfer the longitudinal torque of pinion shaft assembly into lateral torque in the rotatable differential house assembly. 
     4. “Rotatable Differential House Assembly”  17 —is a housing apparatus with the fasteners, bearings, shims cups, and bearings necessary to transfer the lateral torque of the ring gear assembly to the differential bevel and pinion gear set. 
     5. “Differential Bevel and Pinion Gear Set”—is pinion gears, washers, bevel gears, pinion shaft, and locking mechanism necessary to bifurcate the lateral torque communicated from the rotatable differential house assembly  17  and transfer it to the rear axle shaft assembly. 
     6. “Axle housing”—is a body  20  and two shafts  28  where the body is sufficient to be fastened to the drop out third member carrier assembly  1  and with said drop out third member carrier assembly houses  1  the drive pinion assembly  11 , the ring gear assembly  16 , the rotatable differential house assembly  17  with the differential bevel and pinion gear set, and the differential bearing clamp assembly  19 . The two shafts of the axle housing  28  house the rear axle shaft assemblies. 
     7. “Differential Bearing Clamp Assembly”  19 —is two bearing clamps with fasteners on either side of the differential housing that secure the differential bearings to the drop out third member carrier. 
     8. “Rear Axle Shaft Assembly”—is the two shafts, bearings, oil seals, that transfers the lateral torque from the differential bevel and pinion gear set to the first and second tire assemblies. 
     Drop Out Third Member Carrier Assembly 
     One preferred embodiment of said drop out third member carrier assembly  1  has an exterior side  2  and an interior side  3 . Said exterior side  2  is shaped in a convex orientation and faces a drive train of a vehicle. Said interior side  3  is shaped in a concave orientation and faces said body of said axle housing  20 . Said exterior side  2  and interior side  3  have outer edges  4 . Said drop out third member carrier assembly  1  has a top side  5  and a bottom side  6 . Said top side  5  is the vertical half of said drop out third member assembly  1  that abuts the carriage of a vehicle where the input of the drive pinion assembly  11  is on an anterior side of said rear axle assembly  1 . Said bottom side  6  is the vertical half of said drop out third member assembly  1  that faces the ground where the input of the drive pinion assembly  11  is on said anterior of said rear axle assembly. Said drop out third member carrier assembly  1  has a pinion drive side  7  and a non-pinion drive side  8 . Said pinion drive side  7  is the horizontal half of said drop out third member carrier assembly  1  where a portion of the drive pinion assembly  11  substantially travels through it. The non-pinion drive side  8  is the horizontal half of said drop out third member carrier assembly  1  that substantially does not have a portion of the drive pinion assembly  11  traveling through it. In one preferred embodiment said outer edges  4  are substantially symmetrical along a vertical axis and a horizontal axis that respectively divide said top half from said bottom half and said pinion drive side  7  from said non-pinion drive side  8 . In another preferred embodiment, said outer edges  4  have twelve sides and are shaped as a dodecagon. 
     In one preferred embodiment, said drop out third member carrier assembly  1  has an aperture  10  sufficiently large so that a portion of the drive pinion assembly can travel through it. Said aperture is substantially located on the pinion drive side  7 . Said exterior side  2  has a sleeve  12  around said aperture  10  that protrudes from the exterior side  2 . In one preferred embodiment, said sleeve  12  is substantially circular. In one preferred embodiment, said aperture  10  is oriented in a manner sufficient to have a mild hypoid mesh between the drive pinion teeth and the ring gear teeth. Said sleeve  12  has an outer lip  13 . In one preferred embodiment, said outer lip  13  is substantially flat. Around said outer lip  13  there are holes  14  sufficient so fasteners can affix shims to said drop out third member carrier assembly. In one preferred embodiment of the fasteners, said fasteners are bolts. In one preferred embodiment of holes  14 , said holes  14  are equidistantly spaced around the radius of said outer lip  13 . In one preferred embodiment of said holes  14 , there are six said holes  14 . 
     In one preferred embodiment of the invention, said outer edges  4  of said exterior side  2  are rounded sufficient so that the said outer edges  4  are less likely to get stuck on rocks. Around said outer edges  4 , one preferred embodiment has perforations  9  sufficiently large so fasteners can travel through said drop out third member carrier assembly  1  to the body of the axle housing  20  and affix said drop out third member carrier  1  to said body of the axle housing  20 . In one preferred embodiment, said fasteners are bolts. In one preferred embodiment, there are twelve said perforations  9 . In another preferred embodiment, said perforations  9  are symmetrically oriented around said outer edges  4  along said vertical axis and said lateral axis. Another preferred embodiment of invention said twelve perforations  9  are located at the angles of said dodecagon shape of said outer edges  4 . In another preferred embodiment of said invention, the perforations  9  have equidistant depths between the exterior side  2  and the interior side  3  so the same length bolt can be used in each perforation  9 . In another embodiment of said perforations  9 , the material around the perforations  9  is oriented so it is not likely to deform in a manner covering said perforations when struck by an object. 
     One preferred embodiment of said interior side  3  there is an oiling shelf  15  located on a side of said aperture  10  for said drive pinion assembly  11 . In one preferred embodiment said oiling shelf  15  is located on the medial side of said aperture  10  where the medial side is located towards the middle of said drop out third member carrier assembly  1  and conversely the lateral side is located towards said exterior sides  2 . In one preferred embodiment, said oiling shelf  15  is oriented so it provides adequate lubrication even when the top side  5  and bottom side  6  are flipped so that the pinion drive assembly  1  is on the posterior side of the rear gear axle assembly. One preferred embodiment of the oiling shelf  15  is substantially semi-circular. In another preferred embodiment, the oiling shelf  15  is semi-circular with a medially oriented plate oriented in a manner to house said holes  14  of said sleeve  12  so said fasteners can have equidistant length. 
     Said interior side  3  is conversely shaped in a said concave orientation sufficient to carry and partially house the following: said drive pinion assembly  11 , said ring gear assembly  16 , said rotatable differential house assembly  17  with the differential bevel and pinion gear set, and said differential bearing clamp assembly  25 . Said interior side  3  is oriented to reduce bearing movements of said drive pinion bearings  21  and said differential bearings  22 . Said interior side  3  is oriented to reduce deflections between said ring gear assembly  16  and drive pinion assembly  11 . 
     In one embodiment of said drop out third member carrier assembly  1 , there is a passage  23  from the exterior side  2  to the interior side  3  where a load bolt can travel. Said load bolt is oriented so that it can minimize deflections between the pinion drive assembly  11  and the ring gear assembly  1 . In one embodiment of said passage  23 , the passage  23  is located laterally on the non-pinion side  8  of the drop out third member carrier assembly  1 . 
     In one embodiment, said interior side  3  is shaped sufficiently to house a 10.5 inch diameter ring gear. One preferred embodiment of said interior side  3  has a rectangular shaped octagon  33  in the center of the interior side that is concave enough to house said ring gear assembly  16 . In said octagon  33 , two long sides are vertically oriented and communicate with four small angular oriented sides on the two long sides&#39; top sides and bottom sides. Said four small angular oriented sides communicate with two horizontal sides that are smaller than the two long sides and bigger than said four small angular oriented sides. In one preferred embodiment, an inner surface in said octagon  33  is substantially flat. In another preferred embodiment the shape of said octagon  33  is interrupted by said oiling shelf  15  and said medially oriented plate. 
     Said interior side  3  has two mounting platforms  24  for the differential bearing clamp assembly  25 . A first of said mounting platforms  24  is located on said pinion drive side  7  and a second of said mounting platforms  24  is located on said non-pinion drive side  8 . First and second said mounting platforms  24  are located laterally from said octagon  33  and said aperture for the portion said drive pinion assembly  11  and are located medially from said outer edges  4 . Said first and second mounting platforms  24  are designed to house half of two differential bearings  22  and two corresponding bearings caps  26  and affix to said differential bearing clamps  25 . One embodiment of said first and second mounting platforms  24  is each of said platforms  24  has two affixing bases and one semi-circular cavity to house half of one said differential bearing  22  and half of one said differential bearing cap  26 . Said semi-circular cavity is located between said two affixing bases which are oriented vertically above and below said semi-circular cavity. Between first and second said mounting platforms  24 , there is a total of four affixing bases and two said semi-circular cavities. In one embodiment of said affixing bases, there is at least one opening on each affixing base where fasteners can affix said bearing clamps  25  to said affixing bases. One preferred embodiment has two said openings on each of said four affixing bases for a total of eight said openings. Said openings on said affixing bases can have substantially the same depth or different depth to provide weight savings. In one embodiment of the two said semi-circular cavities, the surfaces of said semi-circular cavities are threaded. 
     In one preferred embodiment, said drop out third member carrier  1  has ports  27  that travel from said exterior side  2  to said interior side  3 . Said ports  27  allow for routing for an air locking mechanism. In one embodiment, there is a said port  27  that is on said top side  5  of said drop out third member carrier assembly  1  and a said port  27  on said bottom side  6  of said drop out third member carrier assembly  1 . 
     Said drop out third member carrier assembly  1  can be constructed from a variety of materials including, but not limited to the following: steel, iron, titanium, beryllium, magnesium, copper, nodular iron, and from any metallic element or alloy of any metallic element that provides sufficient strength commonly known to ordinary people skilled in the art. In one preferred embodiment, said third member carrier assembly  1  is constructed from aluminum which has advantages over other materials by being lighter than many materials, but still providing sufficient strength. In another preferred embodiment, said third member carrier assembly  1  is constructed from nodular iron which is also known in the art as ductile iron. Said utilization of nodular iron in the construction has the benefits of dampening harmonics and being more impact resistant than aluminum. 
     Drive Pinion and Ring Gear Assemblies 
     Said drive pinion assembly  1  includes the following components: drive pinion, pinion teeth, cups, bearings, shims, nuts, seals, and spacers. In different embodiments, said drive pinion has teeth sufficient to have the following rotational rate ratio with the ring gear assembly: 3.21:1, 3.42:1, 3.73:1, 4.10:1, 4.56:1, 4.88:1, 5.13:1, and 5.38:1. Said ring gear assembly includes the ring gear with its teeth and fasteners. In one embodiment, said ring gear has a 10.5 inch diameter. In said embodiment, said 10.5 inch diameter ring gear has teeth sufficient to have the following rotational rate ratio with the pinion drive assembly: 3.21:1, 3.42:1, 3.73:1, 4.10:1, 4.56:1, 4.88:1, 5.13:1, and 5.38:1. 
     Rotatable Differential House Assembly with Differential Bevel and Pinion Gear Set 
     Said rotatable differential house assembly  17  includes the following components: a housing apparatus, fasteners, bearings, shims, cups, bearings, and space sufficient to house a differential bevel and pinion gear set. In one embodiment, said rotatable differential house  17  has a space to house a differential locking mechanism and air routing to control said differential locking mechanism. Said differential bevel and pinion gear set includes the following: pinion gears, washers, bevel gears, and pinion shaft. In one embodiment said differential bevel and pinion gear set includes a differential locking mechanism. Said differential locking mechanism in one embodiment is controlled via air routing. 
     Rear Axle Housing 
     Said rear axle housing includes: a body  20 , two shafts  28 , and fasteners to be fastened to a chassis of a vehicle. Said body is shaped sufficient to be fastened to the drop out third member carrier assembly. Said body is also shaped sufficient to house with said drop out third member carrier the following: the drive pinion assembly, the ring gear assembly, the rotatable differential house assembly with the differential bevel and pinion gear set, and the differential bearing clamp assembly. In one embodiment, said body can house with said drop out third member carrier assembly 10.5 inch ring gear. 
     Said body  20  has an internal  29  and external side  30 . Said internal side  29  is shaped in a concave orientation and abuts the drop out third member carrier assembly  1 . Said external side  30  is shaped in a convex orientation and faces the opposite direction of the drive pinion assembly  11 . Said internal side  29  and external sides  30  have outer borders  31 . In one preferred embodiment said outer borders  31  are substantially symmetrical along a vertical axis and a horizontal axis. In another preferred embodiment, said outer borders  31  have twelve sides and are shaped as a dodecagon. 
     Around said outer border  31 , one preferred embodiment has hollows  32  sufficiently large so fasteners can travel through said drop out third member carrier assembly  1  to the body of the axle housing and affix said drop out third member carrier  1  to said body of said axle housing  20 . In one preferred embodiment, said fasteners are bolts. In one preferred embodiment, there are twelve said hollows  32 . In another preferred embodiment, said hollows  32  are symmetrically oriented around said outer borders  31  along said vertical axis and said lateral axis. Another preferred embodiment of invention said twelve hollows  32  are located at the angles of said dodecagon shape of said outer borders  31 . 
     Said shafts of the axle housing  28  are shaped to house the rear axle shaft assemblies. In one preferred embodiment said shafts  28  are tubular traveling from said body of the rear axle housing  20  to first and second wheel assemblies. In addition to said body  20  and said shafts  28 , the rear axle housing includes fasteners to be fastened to the chassis of a vehicle. In one said embodiment the fasteners are bolts and travel through channels in the chassis and rear axle housing affixing them together. 
     Differential Bearing Clamp Assembly 
     Said differential bearing clamp assembly  19  includes the following components: two bearing clamps  25  with fasteners on either side of the differential housing that secure the differential bearings to the drop out third member carrier  1 . In one embodiment, two said bearing clamps  25  can be affixed to two said mounting platforms  24 . Two said bearing clamps  25  are designed to house half of two differential bearings  22  and two corresponding bearings caps and affix to said mounting platforms  24 . One embodiment of said bearing clamps  25  has two affixing legs attached to one semi-circular repository to house half of one said differential bearing and half of one said differential bearing cap. Said semi-circular repository is located between two said affixing legs which abut the mounting platforms  24 . Between two said bearing clamps  25 , there are a total of four affixing legs and two said semi-circular repositories. In one embodiment of said affixing legs, there is at least one pathway on each affixing base where fasteners can affix said bearing clamps to said affixing bases. One preferred embodiment has two said pathways on each of said four affixing legs for a total of eight said openings. In one embodiment of the two said semi-circular repositories, the surfaces of said semi-circular repositories are threaded. 
     Rear Axle Shaft Assembly 
     Said rear axle shaft assembly including the following components: two shafts, bearings, oil seals, that transfers the lateral torque from the differential bevel and pinion gear set to the first and second tire assemblies. 
     Although the foregoing description contains many specifics, these should not be construed as limiting the scope of the invention or of any of the appended claims, but merely as providing information pertinent to some specific embodiments that may fall within the scopes of the invention and the appended claims. Features from different embodiments may be employed in combination. In addition, other embodiments of the invention may also be devised which lie within the scopes of the invention and the appended claims. The scope of the invention is, therefore, indicated and limited only by the appended claims and their legal equivalents. All additions, deletions and modifications to the invention, as disclosed herein, that fall within the meaning and scopes of the claims are to be embraced by the claims.