Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H57/00—General details of gearing
  • F16H57/04—Features relating to lubrication or cooling or heating
  • F16H57/048—Type of gearings to be lubricated, cooled or heated
  • F16H57/0482—Gearings with gears having orbital motion
  • F16H57/0483—Axle or inter-axle differentials
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H57/00—General details of gearing
  • F16H57/04—Features relating to lubrication or cooling or heating
  • F16H57/042—Guidance of lubricant
  • F16H57/0421—Guidance of lubricant on or within the casing, e.g. shields or baffles for collecting lubricant, tubes, pipes, grooves, channels or the like
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H57/00—General details of gearing
  • F16H57/04—Features relating to lubrication or cooling or heating
  • F16H57/042—Guidance of lubricant
  • F16H57/0421—Guidance of lubricant on or within the casing, e.g. shields or baffles for collecting lubricant, tubes, pipes, grooves, channels or the like
  • F16H57/0423—Lubricant guiding means mounted or supported on the casing, e.g. shields or baffles for collecting lubricant, tubes or pipes
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16N—LUBRICATING
  • F16N2210/00—Applications
  • F16N2210/12—Gearings

Definitions

• the invention refers to an arrangement for lubricating an axle gear differential in a motor vehicle according to the preamble to claim 1.
• the invention also concerns a motor vehicle.
• the differential gear In an axle gear, the differential gear needs to be supplied with oil for lubrication, cooling and the removal of harmful particles. It is consequently of major importance to supply the differential with a constant oil flow during operation. Because the design must be as cost-effective as possible and highly efficient, oil pumps are rarely found on axle gears.
• the supply of oil to the differential is achieved by means of splash lubrication from rotating parts that have a submersion depth in the oil sump, or by guiding splashed oil to the intended area.
• the differential gear sits inside a pair of differential cases, which rotate during operation, making it difficult to transport oil without pump pressure outside of the differential cases, into the differential case and finally to the differential gear.
• This flow cannot be controlled by means of splash lubrication because the centrifugal force would cast aside the oil, which must instead to guided to the middle of the differential cases to ensure a constant oil supply during operation.
• US3825099 describes an arrangement for lubricating a differential wherein oil is intended to be supplied to the differential case via an opening in adjustment ring that works in relation to the differential case, and then via a bent metal washer arranged in relation to the outer bearing ring and the wall of the adjusting ring, whereupon a collar formed on the drive axle is sealingly arranged against the central opening of the adjusting ring so as to prevent the oil from running back into the sump, but rather it is guided into the space in the differential case whereupon, by means of rotation of the differential, the oil is guided in to provide a constant flow to lubricate the differential.
• Such an arrangement involving a bent metal washer entails a risk of leakage.
• a collar with associated radii on the drive axle entails a negative fluting effect that significantly degrades the strength of the drive axle.
• One object of the present invention is to achieve an arrangement for lubricating an axle gear of a motor vehicle, which arrangement cost- effectively and with retained strength, enables a constant flow of lubricant to lubricate an axle gear differential with a minimized risk of leakage.
• axle gear differential which axle gear comprises a gear case in which a differential case housing a differential gear is rotatably journaled, wherein lubricant is intended to be supplied to the differential case from a space formed between an adjusting ring working in relation to the differential case and a bearing ring for journaling the differential case, which bearing ring is fixedly fastened to the gear case and comprising an essentially annular lubricant guide that is sealingly against the adjusting ring and the bearing ring, which lubricant guide comprises a hollow space arranged so as, via at least one inlet of the lubricant guide, to be supplied with lubricant and, via at least one outlet, to supply lubricant to the differential case.
• the adjusting ring and drive axle are not affected by the lubricant flow.
• the lubricant guide constitutes a cohesive part and a separate unit, it can be disposed inside the adjusting ring, thereby enabling direct contact between the adjusting ring and the outer bearing ring of the differential case.
• the lubricant guide as a separate part where only the lubricant guide guides the lubricant increases the design freedom for surrounding components, where, for example, the hollowness of the adjusting ring can be optimized for a production-friendly grip. Increasing the design freedom makes it possible to coordinate the surrounding components to a greater extent in accordance with a modularizing concept where, for example, the adjusting ring can be used for both the right and left side of the differential case, which would not otherwise be possible. Because the lubricant guide constitutes a separate part, it can also be mounted securely to the adjusting ring by means of a snap-device in order to facilitate handling during the installation step.
• the lubricant guide comprises a first and a second essentially annular part that together from the hollow space. This enables a simple design of the lubricant guide with an annular running conduit within. This further enables easy installation of the lubricant guide in connection to the adjusting ring and bearing ring.
• the first part is arranged so as to seal against the adjusting ring and the second part is arranged so as to seal against the bearing ring. Simple mounting and effective sealing is achieved thereby.
• said at least one inlet is arranged in connection to the outer periphery of the lubricant guide, and said outlet is arranged in connection to the inner periphery of the lubricant guide. Efficient guidance of the lubricant in through the inlet is achieved thereby, in that the lubricant is forced in, due to the seals and the fact that the inlet through which the lubricant flows is arranged in a lower area, so that when lubricant is filled between adjusting ring and outer bearing ring, the lubricant finds its way into the inlet, whereupon the lubricant level in the oil guide rises. The lubricant level in the oil guide then rises to the level of the outlet, whereupon efficient guidance out through the outlet and into the space in the differential case is enabled.
• said outlet is arranged so as to connect to a space between the differential case and a drive axle that runs through the differential housing. Easy guidance of the lubricant to the space between the differential case and the drive axle for further transport to the lubricant guide and through same is thereby enabled.
• the differential case comprises a recess arranged in connection to said outlet so as to capture lubricant by means of a level difference. Lubricant is thereby prevented from running back, and is instead guided into the space in the differential case for said lubrication.
• lubricant supplied to the differential case from the lubricant guide is arranged so as to be supplied to an essentially conical space that expands inwardly from said outlet to achieve improved distribution of lubricant by means of centrifugal force from the rotation of the differential case. Utilizing the rotation of the differential case in this way provides for efficient guidance of lubricant in the direction toward the differential gear for lubrication of same, so that no pump or corresponding element for pressurizing and pumping the lubricant is needed.
• the space is supplied with surplus lubricant from a space in the differential case, which space is supplied lubricant from said outlet, which lubricant is arranged so as to be supplied to said bearing via a space between the differential case and the lubricant guide. Lubrication of the bearing with bearing rings and rollers is also enabled thereby.
• the inner jacket surface of the differential case comprises, in relation to said drive axle, at least one step for increasing the inner diameter of said space in order to achieve a volume increase in the direction from said lubricant guide.
• the space that is being supplied with lubricant from said outlet comprises an outlet with a throttling function for achieving both the accumulation of a surplus of lubricant volume in the space for bearing lubrication and for lubrication of the differential gear.
• a throttling function for achieving both the accumulation of a surplus of lubricant volume in the space for bearing lubrication and for lubrication of the differential gear.
• Fig. 1 schematically illustrates a motor vehicle according to one embodiment of the present invention
• Fig. 2 schematically illustrates a perspective view of a part of an axel gear for a motor vehicle containing an arrangement for lubricating an axle gear differential according to one embodiment of the present invention
• Fig. 3 schematically illustrates a partially cut-away perspective view of a part of the axle gear with the arrangement in Fig. 2;
• Fig. 4 schematically illustrates a cross-section view in the horizontal plane of a part of the axle gear with the arrangement in Fig. 2;
• Fig. 5 schematically illustrates a cross-section view in the vertical plane of a part of the axle gear with the arrangement in Fig. 2;
• Fig. 6 schematically illustrates a cross section-view in the vertical plane of a part of the axle gear with the arrangement in Fig. 2;
• Fig. 7a schematically illustrates a perspective view of a lubricant guide according to one embodiment of the present invention.
• Fig. 7b schematically illustrates a cross-section view of the lubricant guide in Fig. 7a.
• Fig. 1 schematically illustrates a motor vehicle 1 according to one embodiment of the present invention.
• the exemplary vehicle 1 consists of a heavy vehicle in the form of a goods vehicle.
• the vehicle can consist of any suitable vehicle.
• the vehicle contains an arrangement for lubricating an axle gear according to the present invention.
• the vehicle contains an axle gear I comprising an arrangement for lubricating the axle gear according to the present invention.
• Figs. 2-6 schematically illustrate various views and details of an axle gear I for a motor vehicle comprising an arrangement for lubricating an axle gear differential I according to one embodiment of the present invention.
• the axle gear I comprises an axle bridge 10 with a gear case 20.
• the axle gear I further comprises a differential 30 with a differential case 32 and a differential gear 34, wherein the differential gear 34 is housed in the differential case 32.
• the differential 30, i.e. the differential case 32 with its housed differential gear 34, is rotatably journaled in the gear case 20 by means of bearings.
• the axle gear I comprises a crown gear 22 intended to be brought into toothed engagement with a pinion drive (not shown) for transferring rotational motion from the universal drive shaft of the vehicle to the thus-powered axles X1 , X2 of the vehicle, constituting a first drive axle X1 and a second drive axle X2.
• the crown gear 22 is arranged circumferentially around the differential case 32, constituting a differential shaft.
• the differential 30 is arranged so as to adapt the speed between the drive wheels via the vehicle drive axles X1 , X2 arranged so as to rotate around an axis.
• the gear case 20 is arranged so as to house the crown gear 22 and the pinion (not shown).
• the gear case 20 has an opening 20b through which a pinion shaft (not shown) is arranged so as to run for connection to the universal drive shaft.
• the differential gear 34 of the axle gear I comprises a first differential wheel 34a arranged around the first drive axle X1 , a second differential wheel 34b arranged around the second drive axle X2, a differential case 32 containing a differential spider 35 arranged around the first drive axle X1 , which differential spider has conical spider pinions 36a, 36b for interworking with the first and second differential wheel 34a, 34b.
• the differential spider 35 engages a central section 35c arranged between the first and second drive axle X2 and four bearing journals 35a, 35b that project radially from the central section 35c, two of which are shown in Fig. 3, where respective bearing journals 35a, 35b are essentially perpendicularly displaced relative to adjacent bearing journals 35a, 35b.
• a conical spider pinion 36a, 36b is rotatably arranged around each respective bearing journal 35a, 35b.
• the differential spider 35 is slidably arranged in the differential case 32. Each respective bearing journal 35a, 35b thus lies in slidable contact with the internal surface of the differential case.
• the differential case 32 consequently supports said differential spider 35 with spider pinions 36a, 36b.
• the first differential wheel 34a has a conical toothed section facing the differential spider and arranged so as to be brought into toothed engagement with the spider pinions 36a, 36b.
• the second differential wheel 34b correspondingly has a conical toothed section facing the differential spider 35 and arranged so as to be brought into toothed engagement with the spider pinions 36a, 36b.
• the first differential wheel 34a is connected to the first drive axle X1 via a spline connection X1a.
• the second differential wheel 34b is connected with the second drive axle X2 via a spline connection X2a.
• the axle gear I comprises a bearing cap 24 integrated with the gear case 20 and arranged circumferentially around the differential case 32 in connection to and around the first drive axle X1.
• the bearing cap 24 is arranged so as to support a first differential bearing 44 that is connected with the differential case 32 and arranged so as to run inside the bearing cap 24.
• the first differential bearing 44 consists of a conical roller bearing.
• the first differential bearing 44 comprises an outer bearing ring 44a fixedly connected to the gear case 20 by means of force-fitting.
• the first differential bearing 44 further comprises an inner bearing ring 44b arranged fixedly connected to the differential case 32 by means of force-fitting.
• the first differential bearing 44 further comprises conical rollers 44c arranged between the outer bearing ring 44a and the inner bearing ring 44b to enable rotation of the differential case 32 relative to the gear case 20/bearing cap 24.
• the axle gear I comprises a bearing seat 26 arranged so as circumferentially run around the differential case 32 in connection to and around the second drive axle X2.
• the bearing seat 26 is arranged so as to support a second differential bearing 46 connected with the differential case 32 and arranged so as to run inside the bearing seat 26.
• the axle gear I comprises an adjusting ring 60 that works in relation to the differential case 32.
• the adjusting ring 60 is arranged in connection to the first differential bearing 44.
• the adjusting ring 60 is arranged so as to work in relation to the first differential bearing 44 so as to hold the first differential bearing 44 in place.
• the adjusting ring 60 is threadedly connected with the bearing cap 24/gear case 20 by means of a threaded connection 62, whereupon an outer thread on the adjusting ring 60 is arranged so as to interwork with an inner thread on the bearing case 24/gear case 20.
• Said threaded connection enables axial adjustment of the adjusting ring 60, whereupon the adjusting ring 60 is arranged so as to be adjusted by turning the adjusting ring 60. This enables adjustment of gear backlash between pinion and crown gear 22 of the differential gear 34 by means of thus working in relation to the differential case 32.
• the axle gear I comprises a lubricant sump (not shown) in the axle bridge 10 for lubricating crown gear 22 and pinion.
• the arrangement for lubricating a differential 30 in an axle gear I comprises a lubricant channel 70 arranged on the inner wall 10a of the axle bridge 10.
• the lubricant channel 70 is arranged so as to run along the inner wall 10a.
• the lubricant channel 70 is arranged so as to collect and guide lubricant from the lubricant sump that has been cast up to the inner wall 10a and is running down from the inner wall 10a to a collecting space 80 arranged in connection to the bearing cap 24 for collecting said lubricant O.
• the arrangement for lubricating a differential 30 in the axle gear I comprises a duct 82 that runs from said collecting space 80 through the bearing cap 24/gear case 20 essentially radially inward in the direction toward the first drive axle X2 to a space 86 between the adjusting ring 60 and the outer bearing ring 44a of the first differential bearing 44.
• the duct 82 transitions into a groove 84 that runs internally in the lower hemisphere of the bearing cap 24.
• the internally running semicircular groove 84 for lubricant in the bearing cap 24 has a diameter, as measured from the bottom of the groove 84, that is greater than the outside diameter of the outer bearing ring 44a of the first differential gear 44.
• the arrangement for lubricating a differential 30 in an axle gear I comprises an essentially annular lubricant guide 50 that is sealingly arranged against the adjusting ring 60 and the bearing ring.
• the lubricant guide 50 comprises a hollow space 50a. Said hollow space 50a is arranged so as to run internally around the essentially circular lubricant guide 50.
• the lubricant guide 50 comprises at least one inlet 50b through which the lubricant O is arranged so as to be supplied to the hollow space 50a in the lubricant guide 50.
• the lubricant guide 50 comprises four inlets 50b that are arranged essentially evenly spaced in connection to the outer periphery of the lubricant guide 50.
• the lubricant guide 50 further comprises at least one outlet 50c through which the lubricant O is arranged so as to be supplied to the differential case 32.
• the lubricant guide 50 comprises an outlet 50c arranged in connection to the inner periphery of the lubricant guide 50.
• the lubricant guide 50 is sealingly arranged in relation to the adjusting ring 60 and the outer outer [sic] adjusting ring 44a of the first differential bearing 44.
• the lubricant guide 50 comprises a first essentially annular part 52 and a second essentially annual part 54, which jointly form the hollow space 50a.
• the first and the second parts 52, 54 are arranged so as to be connected by means of a snap-connection 53 to form the lubricant guide 50 with its hollow space 50a.
• the first part of the lubricant guide 50 is arranged so as to seal against the adjusting ring 60.
• the first part comprises a sealing section 52a in the form of a sealing groove or sealing lip arranged peripherally on the first part 52 of the lubricant guide 50.
• the second part 54 of the lubricant guide 50 is arranged so as to seal against the outer bearing ring 44a of the first differential bearing 44.
• the second part 54 comprises a sealing section 54a in the form of a sealing groove or sealing lip arranged peripherally on the second part 54 of the lubricant guide 50.
• the lubricant guide 50 comprises at least one localizing section 55 in the form of a projection arranged in connection to the outer periphery of the lubricant guide 50 for localizing and fitting to the adjusting ring 60.
• the lubricant guide 50 comprises four localizing sections in the form of projections that are spaced essentially evenly along the outer periphery of the lubricant guide.
• the adjusting ring 60 correspondingly comprises at least one localizing section of the form of recesses (not shown) arranged so as to interwork with the localizing sections 55 of the lubricant guide 50 to localize and connect the lubricant guide 50 to the adjusting ring 60. This facilitates mounting of the lubricant guide 50, which is consequently applied when the adjusting ring 60 is threaded in secure connection to the bearing cap 24/gear case 20.
• the lubricant guide 50 has number of inlets 50b spaced uniformly along the outer periphery of the lubricant guide, here four inlets 50b spaced at roughly 90 degree angles from one another, it is ensured that an outlet 50b will be present in the lower area in the space 86 between the adjusting ring 60 and the outer bearing ring 44a in the first differential bearing 44 during mounting, so that lubricant O that is supplied to the space via the duct 82 and the groove 84 will be guided into the inlet and on to the hollow space 50a in the lubricant guide 50.
• the lubricant guide 50 is consequently independent of orientation, which facilitates mounting.
• the outlet 50c is arranged so as to connect to a space between the differential case 32 and the first drive axle X1 running through the differential case 32.
• the first part 52 of the lubricant guide 50 is arranged so as to run in an essentially vertical plane from the periphery and radially inward so as to run essentially horizontally in a central section so as to form its inner periphery.
• the section forming its inner periphery thus constitutes a first collar 52b on the first part 52 of the lubricant guide 50.
• the second part of the lubricant guide 50 is arranged so as to run in an essentially vertical plane from the periphery and radially inward so as to run essentially horizontally in a central section so as to form its inner periphery.
• the section forming its inner periphery thus constitutes a second collar 54b on the second part 54 of the lubricant guide.
• the second collar 54b of the second part 54 is arranged so as to protrude in the direction toward the opening 32a of the differential case 32 and in through the opening 32a of the differential case 32 so that it partially overlaps the inner jacket surface 32b of the opening 32a of the differential case 32 facing the lubricant guide 50 in order to guide lubricant O into the differential case 32.
• the section of the second collar 54b that overlaps the inner jacket surface 32b of the differential case 32 is arranged so as to run essentially parallel thereto and at a distance from the jacket surface 32b, forming a space 32c between the second collar 54b and the jacket surface 32b of the differential case 32.
• the first collar 52b of the first part 52 is arranged so as to protrude in the direction toward the differential case 32 essentially up to the opening 32a of the differential case 32 facing the lubricant guide 50.
• the first collar 52b is consequently arranged so as to protrude a shorter distance than the second collar 54b.
• the first collar 52a has a smaller diameter than the second collar 54b, so that a space is formed between the first collar and the second collar, constituting the outlet 50c of the lubricant guide 50, through which the lubricant O is arranged so as to be guided into the differential case 32.
• the differential case 32 comprises, in connection to the outlet of the lubricant guide 50, a recess 32d arranged so as to capture lubricant O by means of a level difference, as shown in Figs. 5 and 6. This prevents lubricant O from running backward, and it is instead guided into the space 33 in the differential case 32 for said lubrication.
• the level difference is achieved by means of the recess 32d in that the inner material thickness of the differential case is reduced axially along two opposing inner sections of the differential case 32.
• the arrangement for lubricating a differential 30 of the axle gear I comprises an essentially conical space 33 that expands from said outlet 50c of the differential case 32.
• the differential case 32 thus has an essentially conical space 33 that expands inwardly from said outlet 50c to achieve improved outward strewing of lubricant O by means of centrifugal force from the rotation of the differential case 32. Utilizing the rotation of the differential case 32 in this way provides for the efficient guidance of lubricant O in the direction toward the differential gear 34 for lubrication of same, so that no pump or corresponding element for pressurizing and pumping the lubricant is needed.
• the inner jacket surface 32b of the differential case comprises at least one step S1 facing the drive axle to increase the inner diameter of the space 33 in order to increase the volume in the direction away from the lubricant guide 50.
• the inner jacket surface 32b of the differential case 32 facing the drive axle X1 has a step for increasing the inner diameter of the space 33.
• the differential case 32 consequently comprises a first essentially conical space 33a expanding from the outlet and having an angle a1 and a second space 33b expanding from the step in the direction toward the differential gear 34 and having an angle a2.
• the arrangement for lubricating a differential 30 of an axle gear I comprises a outlet 33c arranged in connection to the outer area of the first differential wheel 34a facing lubricant guide 50, which outlet performs a throttling function in order to both achieve the accumulation of a surplus lubricant volume in the space for bearing lubrication and lubrication of the differential gear 34.
• This enables the supply of a sufficient amount of lubricant O for good lubrication of the differential gear 34 before a surplus of lubricant O is achieved for lubricating the first differential bearing 44.
• Efficient lubrication of both differential gear 34 and differential bearing 44 is enabled by means of said throttling function.
• the arrangement for lubricating a differential 30 of the axle gear I consequently comprises the space 32c between the differential case 32 and the second part of the lubricant guide 50, wherein the surplus supplied lubricant O in the space in the differential case 32 is arranged so as to be supplied to the first differential bearing 44 via the space 32c between the differential case 32 and the lubricant guide 50.
• the space 32c consequently constitutes an outlet for surplus lubricant O in the space 33 in the differential case.
• An axle gear I for a motor vehicle has been describe above.
• the axle gear can consist of any suitable driven axle gear, such as a rear axle gear or an axle gear for driving front wheels.
• said lubricant O includes oil.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Details Of Gearings (AREA)
• Retarders (AREA)

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• 2013
  • 2013-01-23 SE SE1350070A patent/SE536949C2/sv unknown
  • 2013-12-19 WO PCT/SE2013/051567 patent/WO2014116162A1/en active Application Filing
  • 2013-12-19 DE DE112013006352.2T patent/DE112013006352B4/de active Active

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