US20170219077A1 - Compact planetary differential gear set arrangement - Google Patents
Compact planetary differential gear set arrangement Download PDFInfo
- Publication number
- US20170219077A1 US20170219077A1 US15/345,219 US201615345219A US2017219077A1 US 20170219077 A1 US20170219077 A1 US 20170219077A1 US 201615345219 A US201615345219 A US 201615345219A US 2017219077 A1 US2017219077 A1 US 2017219077A1
- Authority
- US
- United States
- Prior art keywords
- parts
- pair
- planetary differential
- differential gear
- gear assembly
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
Links
Images
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
- F16H48/00—Differential gearings
- F16H48/06—Differential gearings with gears having orbital motion
- F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
- F16H48/11—Differential gearings with gears having orbital motion with orbital spur gears having intermeshing planet gears
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
- B23K—SOLDERING OR UNSOLDERING; WELDING; CLADDING OR PLATING BY SOLDERING OR WELDING; CUTTING BY APPLYING HEAT LOCALLY, e.g. FLAME CUTTING; WORKING BY LASER BEAM
- B23K15/00—Electron-beam welding or cutting
- B23K15/0046—Welding
-
- 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
- F16H48/00—Differential gearings
- F16H48/38—Constructional details
- F16H48/40—Constructional details characterised by features of the rotating cases
-
- 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
- F16H48/00—Differential gearings
- F16H48/06—Differential gearings with gears having orbital motion
- F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
- F16H2048/106—Differential gearings with gears having orbital motion with orbital spur gears characterised by two sun gears
-
- 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
- F16H48/00—Differential gearings
- F16H48/38—Constructional details
- F16H2048/382—Methods for manufacturing differential gearings
-
- 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
- F16H48/00—Differential gearings
- F16H48/06—Differential gearings with gears having orbital motion
- F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T29/00—Metal working
- Y10T29/49—Method of mechanical manufacture
- Y10T29/49462—Gear making
- Y10T29/49464—Assembling of gear into force transmitting device
Abstract
A compact planetary differential gear set includes first (130A) and second (130B) sun gears, a first set (200A) and a second set (200B) of planet gears (220), and a carrier (160) with a ring gear (190). Enmeshing gear pairs (210) are formed from one planet gear from each set. The first and second planet gear sets enmesh the first and second sun gears, respectively. The ring gear does not extend into an annular region containing the planet gears thereby allowing four or more gear pairs to compactly fit into the annular region. The carrier is a weldment and substantially encloses the sun gears and the planet gears permanently. The differential requires no fasteners or post-weld machining and may have a higher capacity, lower cost, smaller size, lower part number count, and/or lower amounts of material compared with conventional differentials. The differential is suited for motor vehicle applications.
Description
- This application is a Divisional of U.S. patent application Ser. No. 14/342,900, filed 11 Jun. 2014, which is a National Stage Application of PCT/US2012/053672, filed 4 Sep. 2012, which claims benefit of U.S. Patent Application Ser. No. 61/531,611, filed 6 Sep. 2011, and U.S. Patent Application Ser. No. 61/673,439 filed on 19 Jul. 2012 and which applications are incorporated herein by reference. To the extent appropriate, a claim of priority is made to each of the above disclosed applications.
- The present disclosure relates to differential gear sets and planetary differential gear sets. Such differential gear sets are typically found in wheel driven vehicles, such as automobiles and trucks.
- Wheel driven vehicles typically are arranged with a pair of drive wheels positioned opposite each other adjacent opposite sides of the vehicle. The pair of drive wheels is typically driven by a common power source via a common drive train. The pair of drive wheels may be front wheels or rear wheels of the vehicle. When the vehicle is driven around a corner or along a curve, an outside drive wheel of the pair of drive wheels travels a longer distance than an inside drive wheel of the pair of drive wheels, which travels a shorter distance than the outside drive wheel. To accommodate the longer and the shorter distances simultaneously traveled by the opposite drive wheels, the common drive train typically includes a differential gear set.
- In certain all-wheel-drive vehicles, all wheels of the vehicle are drive wheels powered by a common drive train. In certain vehicles, multiple pairs of drive wheel sets (e.g., dual wheels) are positioned opposite each other adjacent opposite sides of the vehicle. In such multi-wheel drive (e.g., multi-drive axle) vehicles, a drive train typically includes a differential gear set between each pair of drive wheels or drive wheel sets (e.g., a first pair of drive wheel sets and a second pair of drive wheel sets). As the first pair of drive wheel sets may have an average travel distance different from the second pair of drive wheel sets, a differential gear set may also be positioned between the first pair of drive wheel sets and the second pair of drive wheel sets (e.g., in a transfer case of the driveline).
- Differential gear sets may be further used in other applications such as packaging machines, linkage arrangements, power dividers, etc.
- Planetary gear sets may include one or more sun gears and one or more planet gears held in position by a carrier. The planet gears typically mesh with one or more of the sun gears. Certain planetary gear sets include a ring gear that is directly coupled to the carrier. Other planetary gear sets include a ring gear that meshes with the planet gears. Certain planetary gears sets may be arranged as differential gear sets. Certain planetary gear sets may be used in multi-speed transmissions.
- Differential gear sets and/or planetary gear sets are often desired that are low in cost, are easily manufactured, include a low number of part numbers, are small in volume, are small in diameter, are narrow in width, are high in torque capacity, and/or are high in stiffness. The present disclosure satisfies these and other desires.
- One aspect of the present disclosure relates to a compact planetary differential gear set with a higher torque capacity in a given size than conventional planetary differential gear sets. The compact planetary differential gear set may have improved torque capacity in a given width, a given diameter, a given volume, a given mass, and/or a given rotational inertia in comparison to conventional differential designs.
- Another aspect of the present disclosure relates to a planetary differential gear set with a lower cost for a given torque capacity than the conventional planetary differential gear sets. The lower cost may result from a low part number count, elimination of fasteners, automated assembly using fixtures, no post-weld machining, and/or a low amount of material used.
- Still another aspect of the present disclosure relates to a planetary differential gear set including, a first sun gear, a second sun gear, a first set of planet gears, a second set of planet gears, and a carrier. The carrier substantially encloses the first sun gear, the second sun gear, the first set of planet gears, and the second set of planet gears. The planetary differential gear set requires no fasteners to operably position the first sun gear, the second sun gear, the first set of planet gears, the second set of planet gears, and the carrier relative to each other when the planetary differential gear set is in use.
- In certain embodiments, such as vehicle axle applications, the first sun gear is adapted to drive a first axle of an automobile and the second sun gear is adapted to drive a second axle of the automobile. The first sun gear may be adapted to drive a first drive shaft of a vehicle and the second sun gear may be adapted to drive a second drive shaft of the vehicle in applications such as vehicle transfer cases. The first set of planet gears may enmesh the first sun gear and the second set of planet gears may enmesh the second sun gear. The first set of planet gears and the second set of planet gears may enmesh each other. The first set of planet gears and the second set of planet gears may be positioned about the sun gears at a common radius.
- Yet another aspect of the present disclosure relates to a planetary differential gear set comprising a sun gear, a set of one or more planet gears, and a carrier having a welded construction that substantially encloses the sun gear and the set of planet gears such that the sun gear and the set of planet gears cannot be removed from the carrier. A method for assembling the planetary differential gear set may include: providing a first portion of the carrier; positioning the sun gear adjacent the first portion of the carrier; positioning the set of planet gears adjacent the first portion of the carrier; positioning a second portion of the carrier adjacent the first portion of the carrier; and, welding the first portion and the second portion of the carrier together.
- In certain embodiments, the welding of the first portion and the second portion of the carrier together in the above method may include electron beam welding. The welding of the first portion and the second portion of the carrier together may introduce only minimal distortion and/or local weld distortion such that no post-weld machining of the planetary differential gear set is required. In certain embodiments, the planetary differential gear set further includes a ring gear. The carrier may include the ring gear, a first portion welded to the ring gear, and a second portion welded to the ring gear. A method for assembling the planetary differential gear set may include: providing the first portion of the carrier; positioning the sun gear adjacent the first portion of the carrier; positioning the set of planet gears adjacent the first portion of the carrier; positioning the ring gear of the carrier adjacent the first portion of the carrier; positioning the second portion of the carrier adjacent the ring gear of the carrier; and, welding the first portion and the second portion of the carrier to the ring gear of the carrier. The welding may include electron beam welding. The sun gear may be adapted to drive a drivetrain shaft (e.g., an axle, a drive shaft, etc.) of a vehicle.
- Still another aspect of the present disclosure relates to a planetary differential gear set including a first sun gear, a second sun gear that is interchangeable with the first sun gear, a first set of planet gears enmeshed with the first sun gear, a second set of planet gears enmeshed with the second sun gear, and a carrier including a first piece and a second piece that are interchangeable with each other. The planet gears of the first set and the second set are interchangeable with each other. The planet gears of the first set and the second set are enmeshed with each other. The first piece forms a major portion of a first side of the carrier, and the second piece forms a major portion of a second side of the carrier. A ring gear may be welded to the first piece and the second piece of the carrier.
- Yet another aspect of the present disclosure relates to a planetary differential gear set including a first sun gear, a second sun gear, at least four intermeshing planet gear pairs, and a carrier. Each of the intermeshing planet gear pairs includes a first planet gear enmeshed with the first sun gear and a second planet gear enmeshed with the second sun gear. The carrier includes a ring gear piece that defines an innermost surface. The innermost surface of the ring gear piece is positioned beyond an outermost cylinder occupied by the intermeshing planet gear pairs.
- In certain embodiments, the innermost surface of the ring gear piece defines a radius that is spaced from the outermost cylinder occupied by the intermeshing planet gear pairs by a radial distance. The radial distance may be less than a thickness of a tooth of the planet gears. The carrier may include a first wall and a second wall that are spaced from each other. A first and a second planet gear of the intermeshing planet gear pairs may each substantially extend between the first wall and the second wall. The first and the second planet gears may each include a reduced diameter portion. The reduced diameter portion of the first planet gear may clear the second sun gear, and the reduced diameter portion of the second planet gear may clear the first sun gear.
- A variety of additional aspects will be set forth in the description that follows. These aspects can relate to individual features and to combinations of features. It is to be understood that both the foregoing general description and the following detailed description are exemplary and explanatory only and are not restrictive of the broad concepts upon which the embodiments disclosed herein are based.
-
FIG. 1 is a perspective view of a planetary differential gear set arrangement according to the principles of the present disclosure; -
FIG. 2 is an exploded perspective view of the planetary differential gear set arrangement ofFIG. 1 illustrating a pair of sun gears, a pair of planet gear sets, a pair of case halves, a ring gear, a set of pins, and a pair of bearing sets; -
FIG. 3 is the perspective view ofFIG. 1 , but with a wedge-shaped cut-away taken that passes through centerlines of two opposite planet gears of the pair of planet gear sets ofFIG. 2 ; -
FIG. 4 is the perspective view ofFIG. 1 , but with a half-cylinder cut-away taken that passes through a centerline of the sun gears ofFIG. 2 and centerlines of two planet gears of one of the planet gear sets ofFIG. 2 ; -
FIG. 5 is the perspective view ofFIG. 1 , but with a chord-shaped cut-away taken that passes through centerlines of a pair of opposite enmeshed planet gears of the pair of planet gear sets ofFIG. 2 ; -
FIG. 6 is the perspective view ofFIG. 1 , but showing only the pair of case halves and the ring gear ofFIG. 2 formed into a carrier; -
FIG. 7 is the perspective view ofFIG. 6 , but with a half-cylinder cut-away taken that passes through a centerline of the carrier; -
FIG. 8 is the perspective view ofFIG. 1 , but showing only the pair of sun gears, the pair of planet gear sets, and the set of pins ofFIG. 2 ; -
FIG. 9 is the perspective view ofFIG. 8 , but with a half-cylinder cut-away taken that passes through the centerline of the sun gears ofFIG. 4 and the centerlines of the two planet gears of the one of the planet gear sets ofFIG. 4 ; -
FIG. 10 is a perspective view illustrating the pair of opposite enmeshed planet gears ofFIG. 5 with a first of the planet gears also enmeshed with a first of the sun gears ofFIG. 2 and a second of the planet gears also enmeshed with a second of the sun gears ofFIG. 2 ; -
FIG. 11 is a plan view illustrating the pair of opposite enmeshed planet gears ofFIG. 5 with the first of the planet gears ofFIG. 10 also enmeshed with the first of the sun gears ofFIG. 10 and the second of the planet gears ofFIG. 10 also enmeshed with the second of the sun gears ofFIG. 10 ; -
FIG. 12 is a plan view of the ring gear ofFIG. 2 ; -
FIG. 13 is a cross-sectional elevation view of the ring gear ofFIG. 2 as called out atFIG. 12 ; -
FIG. 14 is a plan view of one of the sun gears ofFIG. 2 ; -
FIG. 15 is a side view of the one of the sun gears ofFIG. 14 ; -
FIG. 16 is a plan view of one of the planet gears ofFIG. 3 ; -
FIG. 17 is a side view of the one of the planet gears ofFIG. 16 ; -
FIG. 18 is a plan view of one of the case halves ofFIG. 2 showing an outside of the case half; -
FIG. 19 is a cross-sectional side elevation view of the one of the case halves ofFIG. 18 as called out atFIG. 18 ; -
FIG. 20 is another plan view of one of the case halves ofFIG. 2 showing an inside of the case half; -
FIG. 21 is a cross-sectional side elevation view of the one of the case halves ofFIG. 20 as called out atFIG. 20 ; -
FIG. 22 is still another plan view of one of the case halves ofFIG. 2 showing the inside of the case half; and -
FIG. 23 is a cross-sectional side elevation view of the one of the case halves ofFIG. 22 as called out atFIG. 22 . - Reference will now be made in detail to example embodiments of the present disclosure. The accompanying drawings illustrate examples of the present disclosure. When possible, the same reference numbers will be used throughout the drawings to refer to the same or like parts.
- According to the principles of the present disclosure, a compact planetary differential gear set
arrangement 100 may have improved torque capacity in a given width WD (seeFIG. 3 ), a given diameter DD (seeFIG. 1 ), a given volume, a given mass, and/or a given rotational inertia IX-X (seeFIG. 1 ) in comparison to conventional differential designs. The planetary differential gear set 100 may also be built at a lower cost for a given torque capacity than the conventional planetary differential gear sets. The lower cost may result from a lower part number count, elimination of fasteners, automated assembly using fixtures, no post-weld machining, and/or a lower amount of material used. - According to the principles of the present disclosure, the compact planetary differential gear set
arrangement 100 includes acarrier 160 that is assembled over afirst sun gear 130A, asecond sun gear 130B, afirst set 200A of planet gears 220A, asecond set 200B of planet gears 220B and then welded together. By welding thecarrier 160 around thegears gears carrier 160 substantially encloses thefirst sun gear 130A, thesecond sun gear 130B, thefirst set 200A of planet gears 220A, and thesecond set 200B of planet gears 220B. As thecarrier 160 is a weldment, thecarrier 160 permanently encloses (e.g., encases) thegears gears carrier 160 are provided hereinafter. - According to the principles of the present disclosure, the planetary differential gear set
arrangement 100 includes a low number of part numbers. In particular, thefirst sun gear 130A and thesecond sun gear 130B may be interchangeable with each other (i.e., have the same part number). Thefirst sun gear 130A and thesecond sun gear 130B may collectively be known as sun gear 130 (seeFIGS. 14 and 15 ). In addition, the planet gears 220A and the planet gears 220B may be interchangeable with each other (seeFIGS. 8 and 9 ). Theplanet gear 220A and theplanet gear 220B may collectively be known as planet gear 220 (seeFIGS. 16 and 17 ). In addition, thecarrier 160 may include afirst piece 170A and asecond piece 170B that are interchangeable with each other (seeFIGS. 1-4 and 7 ) and also include aring gear 190. Thefirst piece 170A and thesecond piece 170B may collectively be known as carrier piece 170 (seeFIGS. 18-23 ). Furthermore, the planet gears 220 may be rotatably mounted onpins 260 that are all interchangeable with each other, and thedifferential arrangement 100 may be rotatably mounted on a pair ofidentical bearings 270. Thus, as illustrated, the planetary differential gear setarrangement 100 need only include a first part,sun gear 130; a second part,carrier piece 170; a third part,ring gear 190; a fourth part,planet gear 220; a fifth part,pin 260; and a sixth part, bearing 270. Further details of part commonality are provided hereinafter. - According to the principles of the present disclosure, the compact planetary differential gear set
arrangement 100 includes a compact radial arrangement. In particular, as illustrated atFIG. 4 , the sun gears 130, 130A, 130B operate within a radial region RS from a centerline CL of the differential gear set 100. The planet gears 220, 220A, 220B operate within an annular region AP. And, thering gear 190 operates within an annular region AR. As depicted, the annular region AP overlaps the radial region RS by an amount sufficient to allow meshing of the sun gears 130 with the planet gears 220. As depicted, a clearance CP exists between the annular region AP and the annular region AR. The clearance CP can be quite small and thereby contribute to radial compactness of the planetary differential gear setarrangement 100. In the depicted embodiment, the clearance CP may be less than a thickness tT of a tooth T of any one and/or all of thegears FIG. 11 ). - Radial and/or axial compactness in proportion to torque capacity of the planetary differential gear set
arrangement 100 may be accomplished by selecting appropriate gear proportions of thegears gears gears gears gears gears gears gears gears gears arrangement 100. In other embodiments, helical gears and/or other gears may be used for thegears gears - In certain embodiments, as depicted, choosing a helical gear as the
ring gear 190 may be desired. A pinion gear that meshes with thering gear 190 may have a high rotational velocity when the vehicle is normally operated. The high velocity may generate significant undesired noise if straight spur gears were used as the pinion gear and thering gear 190. The pair of thebearings 270 may carry thrust loads generated by the pinion gear and thering gear 190. The pair of thebearings 270 may further carry separating loads generated by the pinion gear and thering gear 190. - Choosing an appropriate number of gear teeth T of the
gears arrangement 100. In the depicted embodiment, the sun gears 130 include 24 gear teeth T, thering gear 190 includes 56 gear teeth T, and the planet gears 220 include 10 gear teeth T. Choosing an appropriate ratio of pitch diameters of thegears arrangement 100. In the depicted embodiment, the ratio of the pitch diameter of the sun gears 130 to the pitch diameter of the planet gears 220 is 12:5. - The welding of the
carrier 160 may increase the radial and/or axial compactness in proportion to torque capacity and thereby contribute to compactness of the planetary differential gear setarrangement 100. In particular, as depicted atFIG. 7 , a weld W joins each of thefirst piece 170A and thesecond piece 170B to thering gear 190. In certain embodiments, a weld W may join thefirst piece 170A and thesecond piece 170B to each other. In the illustrated embodiment, the welds W are made by electron beam welding. Electron beam welding results in the welds W occupying only a thin radial region of the planetary differential gear set 100. In addition, electron beam welding results in: a small heat affected zone; substantially no distortion, low distortion, and/or distortion that is locally limited; no detempering of the teeth T of thegears ring gear 190; no post-weld machining of the planetary differential gear set 100; and allowing a relativelythin gear base 196 of the ring gear 190 (seeFIGS. 7, 12, and 13 ). Welding may further distribute stresses within thecarrier 160, including thering gear 190 and thepins 260, more uniformly than conventional methods (e.g., fasteners). This may allow less material to be used and/or further contribute to compactness of the planetary differential gear setarrangement 100. This may further increase stiffness of the planetary differential gear setarrangement 100. - Using no fasteners may increase the radial and/or axial compactness in proportion to torque capacity and thereby contribute to radial compactness of the planetary differential gear set
arrangement 100. In particular, fasteners (e.g., rivets, threaded fasteners, etc.) and their associated holes, bosses, flanges, etc. typically occupy both radial and axial space. - As depicted, positioning centerlines CLP of the
first set 200A ofplanet gears 220A and thesecond set 200B of planet gears 220B at a common radius RP about the centerline CL of the differential gear set 100 and the sun gears 130A, 130B may increase the radial and/or axial compactness in proportion to torque capacity and thereby contribute to radial compactness of the planetary differential gear set arrangement 100 (seeFIGS. 4 and 20 ). By positioning the centerlines CLP of all of the planet gears 220 at the common radius RP, the common radius RP can be a minimum radius consistent with the required torque capacity of the planetary differential gear setarrangement 100. In certain prior art planetary differential gear sets, a centerline radius of a first planetary gear set is different from a centerline radius of a second planetary gear set and thereby results in radial space being consumed to accommodated the larger of the centerline radii. Notwithstanding, in certain other embodiments of the planetary differential gear setarrangement 100, the centerlines CLP of thefirst set 200A ofplanet gears 220A and thesecond set 200B of planet gears 220B may be positioned at different radii. - According to the principles of the present disclosure, the planetary differential gear set
arrangement 100 may be configured to include at least four intermeshing planet gear pairs 210 1-4 (seeFIGS. 5, 8, 10, and 11 ). Such configuration may be made possible, at least in part, from the compacting features disclosed herein. Certain prior art planetary differential gear sets include only three planet gear pairs due, at least in part, to non-efficient used of space. By including more than three planet gear pairs, additional torque capacity is gained for the planetary differential gear setarrangement 100. - In particular detail, each of the intermeshing planet gear pairs 210 includes one of the first planet gears 220A enmeshed with the
first sun gear 130A and one of the second planet gears 220B enmeshed with thesecond sun gear 130B. As depicted, thefirst planet gear 220A meshes with thefirst sun gear 130A along an axial zone ZA generally corresponding to a width of the teeth T of thefirst sun gear 130A, and thesecond planet gear 220B meshes with thesecond sun gear 130B along an axial zone ZB generally corresponding to a width of the teeth T of thesecond sun gear 130B. Each of the intermeshing planet gear pairs 210 intermeshes within an axial zone ZC generally corresponding to an axial space between the teeth T of thefirst sun gear 130A and the teeth T of thesecond sun gear 130B. In particular, thefirst planet gear 220A of the intermeshingplanet gear pair 210 meshes with thesecond planet gear 220B of the same intermeshingplanet gear pair 210. A tooth pitch, pitch circle, tooth form, etc. of thefirst planet gear 220A may remain the same along a width of its teeth T and across the axial zones ZA and ZC. Likewise, a tooth pitch, pitch circle, tooth form, etc. of thesecond planet gear 220B may remain the same along a width of its teeth T and across the axial zones ZB and ZC. - Turning now to
FIGS. 12 and 13 , thering gear 190 will be described in detail. As depicted, thering gear 190 extends between afirst side 192A and asecond side 192B. The first andsecond sides ring gear 190 generally extend between the first andsecond sides ring gear 190 also extend from anouter perimeter 194 of thering gear 190 to thegear base 196. Thegear base 196 radially extends between the teeth T of thering gear 190 and aninnermost surface 198 of thering gear 190. As depicted, theinnermost surface 198 is positioned beyond an outermost cylinder that is occupied by the planet gears 220 (i.e., an outer cylinder of the annular region AP). - The
gear base 196 may serve as a structural support for the teeth T of thering gear 190, as a locating and stopping feature for thefirst piece 170A and thesecond piece 170B, as a joining piece for thefirst piece 170A and thesecond piece 170B, and as a weld pad that isolates the teeth T of thering gear 190 from weld distortion and a heat affected zone of the welds W. As depicted, thegear base 196 includes a firstcylindrical surface 250A and a secondcylindrical surface 250B. The firstcylindrical surface 250A may be a first high precision cylindrical surface, and the secondcylindrical surface 250B may be a second high precision cylindrical surface. The high precision cylindrical surfaces 250A, 250B may be capable of holding a press fit. The cylindrical surfaces 250A, 250B may be concentric with each other and/or with theinnermost surface 198 of thering gear 190. As depicted, thegear base 196 includes afirst shoulder stop 252A and asecond shoulder stop 252B. The shoulder stops 252A, 252B extend radially inwardly from thecylindrical surfaces innermost surface 198 of thering gear 190. The shoulder stops 252A, 252B may be separated from each other by a recessedarea 254. The recessedarea 254 may include a thirdcylindrical surface 254 with generally the same diameter as thecylindrical surfaces cylindrical surfaces 250A and/or 250B may be concentric with the thirdcylindrical surface 254. The shoulder stops 252A, 252B may be positioned symmetrically about thering gear 190 along the centerline CL of the differential gear set 100, the sun gears 130A, 130B, and thering gear 190. Thering gear 190 may include agroove 256. Thegroove 256 may be positioned on thesecond side 192B and may serve as an indicator of thesecond side 192B and may therefore serve as an orientation indicator of the planetary differential gear setarrangement 100. - Turning now to
FIGS. 14 and 15 , thesun gear 130 will be described in detail. As depicted, thesun gear 130 extends between afirst side 132 and asecond side 134. The first andsecond sides sun gear 130 and the centerlines CLP of the planet gears 220. As depicted, the teeth T of thesun gear 130 generally extend between thefirst side 132 and amedial plane 136. The teeth T of thesun gear 130 generally radially extend between agear base 138 and anouter perimeter 140 of thesun gear 130. A reduceddiameter portion 142 extends between themedial plane 136 and thesecond side 134. The reduceddiameter portion 142 of each of the sun gears 130A, 130B forms about half of the axial zone ZC and allows the teeth T of the planet gears 220 to extend within a cylinder defined by theouter perimeter 140 without meshing with the teeth T of thesun gear 130. Thegear base 138 radially extends between the teeth T of thesun gear 130 and aninnermost surface 144 of thesun gear 130. As depicted, theinnermost surface 144 is included on afemale spline 146 that is adapted to rotationally couple to a male spline of a drivetrain shaft (e.g., an axle, a drive shaft, etc.) of a vehicle. - Turning now to
FIGS. 16 and 17 , theplanet gear 220 will be described in detail. As depicted, theplanet gear 220 extends between afirst side 222 and asecond side 224. The first andsecond sides sun gear 130 and the centerlines CLP of the planet gears 220. As depicted, the teeth T of theplanet gear 220 generally extend between thefirst side 222 and amedial plane 226. The teeth T of theplanet gear 220 generally radially extend between agear base 228 and anouter perimeter 230 of theplanet gear 220. A reduceddiameter portion 232 extends between themedial plane 226 and thesecond side 224. The reduceddiameter portion 232 of the planet gears 220 extends over the axial zones ZA or ZB and allows the teeth T of thesun gear outer perimeter 230 without meshing with the teeth T of theplanet gear gear base 228 radially extends between the teeth T of theplanet gear 220 and an innermost surface 234 of theplanet gear 220. As depicted, the innermost surface 234 includes a bearing surface that is adapted to rotatably mount to thepins 260. The reduceddiameter portion 232 of thefirst planet gear 220A may clear thesecond sun gear 130B, and the reduceddiameter portion 232 of thesecond planet gear 220B may clear thefirst sun gear 130A. - Turning now to
FIGS. 18-23 , thecarrier piece 170 will be described in detail. As depicted, thecarrier piece 170 extends between afirst side 172 and asecond side 174. The first andsecond sides sun gear 130 and thecarrier piece 170 and the centerlines CLP of the planet gears 220. As depicted, thecarrier piece 170 includes a firstcylindrical surface 240 and a secondcylindrical surface 180. The firstcylindrical surface 240 may be a first high precision cylindrical surface, and the secondcylindrical surface 180 may be a second high precision cylindrical surface. The high precisioncylindrical surfaces cylindrical surfaces carrier piece 170 includes a first stop 242 (e.g., a shoulder stop) and a second stop 182 (e.g., a shoulder stop). Thestop 242 extends radially inwardly from thecylindrical surface 240. Thestop 182 extends radially outwardly from thecylindrical surface 180. Thestops FIG. 23 ). The distance DC may be a high precision distance. The shoulder stops 182, 242 of thefirst piece 170A may be positioned symmetrically with respect to the shoulder stops 182, 242 of thesecond piece 170B about thering gear 190 along the centerline CL of the differential gear set 100, the sun gears 130A, 130B, and thering gear 190. The shoulder stops 182, 242 of thefirst piece 170A may be positioned symmetrically with respect to the shoulder stops 182, 242 of thesecond piece 170B about the planetary differential gear setarrangement 100 along the centerline CL. - As depicted, the
carrier piece 170 may be stamped, spun, and/or forged from a single piece of raw material. The raw material may be a plate, a billet, a tube, etc. The stamping, spinning, and/or forging may work harden thecarrier piece 170. In other embodiments, thecarrier piece 170 may be a casting, a machined piece, etc. In certain embodiments, a portion or all of thecarrier piece 170 may be stress and/or strain relieved (e.g., by heating). In certain embodiments, a portion or all of thecarrier piece 170 may be shot-peened. As depicted, thecarrier piece 170 generally defines awall 178 with a wall thickness tW. The wall thickness tW may vary or the wall thickness tW may remain substantially constant. Thewall 178 may form at least a portion of thecylindrical surfaces stops wall 178 may form at least a portion of aradial portion 176 and/or alateral portion 186 of thecarrier piece 170. Theradial portion 176 of thefirst piece 170A may form afirst side 162A, and theradial portion 176 of thesecond piece 170B may form asecond side 162B of a hub (seeFIG. 1 ). At least a portion of thecylindrical surface 180 may form asnout 184 upon which thebearing 270 may be mounted (seeFIG. 21 ). Thebearing 270 may bottom against thestop 182 and thereby be located by thestop 182. By welding thecarrier piece 170 to thering gear 190 and forming thelateral portion 186 on thecarrier piece 170, the planet gears 220 may be separated (i.e., spaced) from thering gear 190 by as little as the wall thickness tW. - The
carrier 160 may include afirst wall 164A and asecond wall 164B formed by insides of thefirst side 162A and thesecond side 162B, respectively. Thewalls first wall 164A and thesecond wall 164B. - As depicted at
FIGS. 18-23 , theradial portion 176 include a series of pin holes 266, a series ofholes 268A, a series ofholes 268B, and a series ofholes 268C. As depicted, theholes 268C extend beyond theradial portion 176 and into thelateral portion 186. As depicted, theholes holes hole 268C includes a round portion and a slot-shaped portion that extends to the lateral portion 186 (see alsoFIG. 6 ). In other embodiments, theholes 268C may have other shapes. In the depicted embodiment, the pin holes 266 mount thepins 260. In particular, the pin holes 266 of thefirst piece 170A mountfirst end portions 262A of thepins 260, and the pin holes 266 of thesecond piece 170B mountsecond end portions 262B of the pins 260 (seeFIG. 2 ). Theholes carrier piece 170, and/or may improve lubrication and oil flow. The tailored stiffness of thecarrier piece 170 may accommodate press fitting the firstcylindrical surface 240 into thecylindrical surfaces carrier piece 170 may accommodate a lower tolerance of the firstcylindrical surface 240 and/or thecylindrical surfaces - In the depicted embodiment, the
lateral portion 186 undulates andforms pockets 188 centered on the pin holes 266. Thepockets 188 may each house at least a portion of one of the planet gears 220. By undulating, thelateral portion 186 may stiffen thecarrier piece 170 and thereby stiffen the planetary differential gear setarrangement 100. By undulating, thelateral portion 186 may reduce rotational inertia. - In the depicted embodiment, the differential gear set 100, including the pinion gear, is governed by the equation
-
K×(V 1 +V 2)/2=V 3 - where K is a gear ratio of the pinion and ring gear set, V1 is a rotational velocity of the
first sun gear 130A, V2 is a rotational velocity of thesecond sun gear 130B, and V3 is a rotational velocity of the pinion gear that drives thering gear 190 of thecarrier 160. - In the depicted embodiment, the differential gear set 100, excluding the pinion gear, is governed by the equation
-
(V 1 +V 2)/2=V 3 - where V1 is the rotational velocity of the
first sun gear 130A, V2 is the rotational velocity of thesecond sun gear 130B, and V3 is a rotational velocity of thecarrier 160. - In other embodiments, the differential gear set 100 may be governed by the equation
-
(n 1 ×V 1 +n 2 ×V 2)=(n 1 +n 2)×V 3 - where n1 and n2 are gear ratios of the differential gear set 100, V1 is a rotational velocity of a first input/
output member 130A, V2 is a rotational velocity of a second input/output member 130B, and V3 is a rotational velocity of a third input/output member (e.g., a pinion). - A method for assembling the planetary differential gear set 100 may include one or more of the steps below. The steps need not necessarily be performed in the order in which they appear. All of the steps need not necessarily be performed. Additional steps may be added. 1) Provide the
first piece 170A of thecarrier 160. 2) Position thefirst sun gear 130A adjacent thefirst piece 170A. In particular, position thefirst side 132 of thefirst sun gear 130A adjacent thefirst wall 164A of thefirst piece 170A with the centerline CL of thefirst sun gear 130A aligned with the centerline CL of the first carrier piece 170A. 3) Position thefirst set 200A of the planet gears 220A adjacent thefirst piece 170A. In particular, position thefirst side 222 of the planet gears 220A adjacent thefirst wall 164A of thefirst piece 170A with the centerline CLP of each of the planet gears 220A aligned with a corresponding center of one of the pin holes 266. 4) Position thering gear 190 adjacent thefirst piece 170A. In particular, position the firstcylindrical surface 250A around the firstcylindrical surface 240 and move and/or press thering gear 190 and thefirst piece 170A together until thefirst stop 242 abuts the first shoulder stop 252A. 5) Position thesecond sun gear 130B adjacent thefirst sun gear 130A. In particular, position thesecond sides 134 of the sun gears 130A and 130B adjacent each other with their centerlines CL aligned. 6) Position thesecond set 200B of the planet gears 220B adjacent thefirst set 200A. In particular, position thesecond side 224 of the planet gears 220B adjacent thefirst wall 164A of thefirst piece 170A with the centerline CLP of each of the planet gears 220B aligned with a corresponding center of one of the pin holes 266. 7) Position thesecond piece 170B of thecarrier 160 adjacent thering gear 190. In particular, position the secondcylindrical surface 250B around the secondcylindrical surface 240 and move and/or press thering gear 190 and thesecond piece 170B together until thefirst stop 242 abuts thesecond shoulder stop 252B while the centerline CLP of each of the planet gears 220 is aligned with a corresponding center of one of the pin holes 266 of the second piece 170B. 8) Secure and/or position some or all of the above parts with a fixture. 9) Insert and/or press thepins 260 into and/or through theholes 266, 234 with a bearing surface 264 (seeFIG. 2 ) of each of thepins 260 engaging a corresponding one of the bearing surfaces 234 of the planet gears 220. 10) Form the weld W between thefirst piece 170A and thering gear 190. 11) Form the weld W between thesecond piece 170B and thering gear 190. 12) Weld thefirst piece 170A and thesecond piece 170B of thecarrier 160 together. 13) Form a weld WP between thefirst piece 170A and thepins 260. 14) Form a weld WP between thesecond piece 170B and thepins 260. And/or, 15) remove the fixture. - As mentioned above, the above steps do not necessarily need to be preformed in the order listed. Some or all of the steps may be performed substantially simultaneously. Some of the above steps may be omitted. Other steps may be added. The welding may include electron beam welding.
- In one example, the width WD (i.e., hub span) can be shown to be about 54% of a width of a typical differential mechanism with the same torque capacity. The overall diameter DD can be about the same as the typical differential mechanism, but weight of the planetary differential gear set
arrangement 100 can be about 88% of the typical differential mechanism, including thering gear 190. In certain embodiments of the planetary differential gear setarrangement 100, torque bias can be one-to-one and torque capacity can be the same or greater than the typical differential mechanism. In certain embodiments, the planetary differential gear setarrangement 100 may be a compact open differential. In certain embodiments, the planetary differential gear setarrangement 100 may have near zero bias. In certain embodiments, the planetary differential gear setarrangement 100 may be configured as a limited slip, a viscous coupled, and/or a locking differential and include corresponding components. In the depicted embodiment, thebearings 270 are roller bearings. - In certain embodiments, such as vehicle axle and/or transfer case applications, the
first sun gear 130A is adapted to drive a first drivetrain shaft (e.g., an axle, a drive shaft, etc.) of a vehicle, and thesecond sun gear 130B is adapted to drive a second drivetrain shaft (e.g., an axle, a drive shaft, etc.) of the vehicle. - Various modifications and alterations of this disclosure will become apparent to those skilled in the art without departing from the scope and spirit of this disclosure, and it should be understood that the scope of this disclosure is not to be unduly limited to the illustrative embodiments set forth herein.
Claims (21)
1-20. (canceled)
21. A planetary differential gear assembly having a first input/output, a second input/output, a third input/output, a first bearing mount, and a second bearing mount, the planetary differential gear assembly consisting essentially of:
a pair of interchangeable first parts, the first parts including a set of gear teeth and an input/output, the input/output of a first one of the pair of first parts being the first input/output of the planetary differential gear assembly, and the input/output of a second one of the pair of first parts being the second input/output of the planetary differential gear assembly;
a pair of interchangeable second parts, the second parts including a bearing mount, a plurality of pin mounts, and a ring gear mount, the bearing mount of a first one of the pair of second parts being the first bearing mount of the planetary differential gear assembly, and the bearing mount of a second one of the pair of second parts being the second bearing mount of the planetary differential gear assembly;
a single third part, the third part including a set of ring gear teeth, the set of ring gear teeth being the third input/output of the planetary differential gear assembly, and the third part including a pair of mounts, a first one of the pair of mounts mounted to the ring gear mount of the first one of the pair of second parts, and a second one of the pair of mounts mounted to the ring gear mount of the second one of the pair of second parts;
a plurality of interchangeable fourth parts, the fourth parts including a set of planet gear teeth and an interior bearing surface, the fourth parts arranged in a plurality of intermeshing planet gear pairs, each of the intermeshing planet gear pairs including a first one of the plurality of fourth parts enmeshed with the first one of the pair of first parts and a second one of the plurality of fourth parts enmeshed with the second one of the pair of first parts;
a plurality of interchangeable fifth parts, the fifth parts including a first portion that mounts in one of the pin mounts of the first one of the pair of second parts, a second portion that mounts in one of the pin mounts of the second one of the pair of second parts, and a bearing surface that rotatably mounts the interior bearing surface of one of the plurality of fourth parts; and
a plurality of welded joints between the first one of the pair of second parts and the third part, between the second one of the pair of second parts and the third part, between the first portion of the fifth parts and the first one of the pair of second parts, and/or between the second portion of the fifth parts and the second one of the pair of second parts.
22. The planetary differential gear assembly of claim 21 , wherein the first part is a sun gear.
23. The planetary differential gear assembly of claim 21 , wherein the input/output of the first part is internal and the set of gear teeth is external.
24. The planetary differential gear assembly of claim 21 , wherein the input/output of the first part includes a spline.
25. The planetary differential gear assembly of claim 21 , wherein the set of gear teeth of the first part are a set of straight spur gear teeth.
26. The planetary differential gear assembly of claim 21 , wherein the ring gear mount includes a continuous outside cylindrical surface and a shoulder stop that extends radially inwardly from the cylindrical surface.
27. The planetary differential gear assembly of claim 21 , wherein each of the pair of mounts includes a continuous inside cylindrical surface and a shoulder stop that extends radially inwardly from the cylindrical surface.
28. The planetary differential gear assembly of claim 21 , wherein each of the plurality of fourth parts longitudinally extends between the first one of the pair of second parts and the second one of the pair of second parts.
29. The planetary differential gear assembly of claim 21 , wherein the first input/output is adapted to drive a first drive shaft of a vehicle and the second input/output is adapted to drive a second drive shaft of the vehicle.
30. The planetary differential gear assembly of claim 21 , wherein the plurality of welded joints introduce only minimal distortion such that no post-weld machining of the planetary differential gear assembly is required.
31. The planetary differential gear assembly of claim 21 , wherein none of the first parts and the fourth parts can be removed from the planetary differential gear assembly.
32. The planetary differential gear assembly of claim 21 , wherein the plurality of welded joints includes at least one circular welded joint that extends around a circular perimeter and wherein the pair of first parts and the plurality of fourth parts are all positioned within the at least one circular perimeter.
33. The planetary differential gear assembly of claim 21 , wherein the first one of the pair of second parts includes a first wall and the second one of the pair of second parts includes a second wall that is spaced from the first wall, wherein each of the plurality of fourth parts longitudinally extends between the first wall and the second wall.
34. The planetary differential gear assembly of claim 33 , wherein the first one of the pair of first parts longitudinally extends from the first wall to the second one of the pair of first parts and wherein the second one of the pair of first parts longitudinally extends from the second wall to the first one of the pair of first parts.
35. A planetary differential gear assembly having a first input/output, a second input/output, a third input/output, a first bearing mount, and a second bearing mount, the planetary differential gear assembly comprising:
a pair of interchangeable first parts, the first parts including a set of gear teeth and an input/output, the input/output of a first one of the pair of first parts being the first input/output of the planetary differential gear assembly, and the input/output of a second one of the pair of first parts being the second input/output of the planetary differential gear assembly;
a pair of interchangeable second parts, the second parts including a bearing mount, a plurality of pin mounts, and a ring gear mount, the bearing mount of a first one of the pair of second parts being the first bearing mount of the planetary differential gear assembly, and the bearing mount of a second one of the pair of second parts being the second bearing mount of the planetary differential gear assembly;
a single third part, the third part including a set of ring gear teeth, the set of ring gear teeth being the third input/output of the planetary differential gear assembly, and the third part including a pair of mounts, a first one of the pair of mounts mounted to the ring gear mount of the first one of the pair of second parts, and a second one of the pair of mounts mounted to the ring gear mount of the second one of the pair of second parts;
a plurality of interchangeable fourth parts, the fourth parts including a set of planet gear teeth and an interior bearing surface, the fourth parts arranged in a plurality of intermeshing planet gear pairs, each of the intermeshing planet gear pairs including a first one of the plurality of fourth parts enmeshed with the first one of the pair of first parts and a second one of the plurality of fourth parts enmeshed with the second one of the pair of first parts;
a plurality of interchangeable fifth parts, the fifth parts including a first portion that mounts in one of the pin mounts of the first one of the pair of second parts, a second portion that mounts in one of the pin mounts of the second one of the pair of second parts, and a bearing surface that rotatably mounts the interior bearing surface of one of the plurality of fourth parts; and
a plurality of welded joints between the first one of the pair of second parts and the third part, between the second one of the pair of second parts and the third part, between the first portion of the fifth parts and the first one of the pair of second parts, and/or between the second portion of the fifth parts and the second one of the pair of second parts.
36. The planetary differential gear assembly of claim 35 , wherein the planetary differential gear assembly consists essentially of the pair of interchangeable first parts, the pair of interchangeable second parts, the single part, the plurality of interchangeable fourth parts, and the plurality of interchangeable fifth parts.
37. The planetary differential gear assembly of claim 35 , wherein the each of the interchangeable first parts is a sun gear, the single third part is a ring gear, and the plurality of interchangeable fourth parts are planet gears.
38. A planetary differential gear assembly having a first input/output, a second input/output, a third input/output, a first bearing mount, and a second bearing mount, the planetary differential gear assembly comprising:
a pair of interchangeable first parts consisting essentially of a set of gear teeth and an input/output, the input/output of a first one of the pair of first parts being the first input/output of the planetary differential gear assembly, and the input/output of a second one of the pair of first parts being the second input/output of the planetary differential gear assembly;
a pair of interchangeable second parts consisting essentially of a bearing mount, a plurality of pin mounts, and a ring gear mount, the bearing mount of a first one of the pair of second parts being the first bearing mount of the planetary differential gear assembly, and the bearing mount of a second one of the pair of second parts being the second bearing mount of the planetary differential gear assembly;
a single third part consisting essentially of a set of ring gear teeth, the set of ring gear teeth being the third input/output of the planetary differential gear assembly, and the third part including a pair of mounts, a first one of the pair of mounts mounted to the ring gear mount of the first one of the pair of second parts, and a second one of the pair of mounts mounted to the ring gear mount of the second one of the pair of second parts;
a plurality of interchangeable fourth parts consisting essentially of a set of planet gear teeth and an interior bearing surface, the fourth parts arranged in a plurality of intermeshing planet gear pairs, each of the intermeshing planet gear pairs including a first one of the plurality of fourth parts enmeshed with the first one of the pair of first parts and a second one of the plurality of fourth parts enmeshed with the second one of the pair of first parts;
a plurality of interchangeable fifth parts consisting essentially of a first portion that mounts in one of the pin mounts of the first one of the pair of second parts, a second portion that mounts in one of the pin mounts of the second one of the pair of second parts, and a bearing surface that rotatably mounts the interior bearing surface of one of the plurality of fourth parts; and
a plurality of welded joints consisting essentially of welded joints between the first one of the pair of second parts and the third part, between the second one of the pair of second parts and the third part, between the first portion of the fifth parts and the first one of the pair of second parts, and/or between the second portion of the fifth parts and the second one of the pair of second parts.
39. The planetary differential gear assembly of claim 38 , wherein the each of the interchangeable first parts is a sun gear, the single third part is a ring gear, and the plurality of interchangeable fourth parts are planet gears.
40. The planetary differential gear assembly of claim 38 , wherein the first one of the pair of second parts includes a first wall and the second one of the pair of second parts includes a second wall that is spaced from the first wall, wherein each of the plurality of fourth parts longitudinally extends between the first wall and the second wall, wherein the first one of the pair of first parts longitudinally extends from the first wall to the second one of the pair of first parts, and wherein the second one of the pair of first parts longitudinally extends from the second wall to the first one of the pair of first parts.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US15/345,219 US20170219077A1 (en) | 2011-09-06 | 2016-11-07 | Compact planetary differential gear set arrangement |
Applications Claiming Priority (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US201161531611P | 2011-09-06 | 2011-09-06 | |
US201261673439P | 2012-07-19 | 2012-07-19 | |
PCT/US2012/053672 WO2013036483A1 (en) | 2011-09-06 | 2012-09-04 | Compact planetary differential gear set arrangement |
US201414342900A | 2014-06-11 | 2014-06-11 | |
US15/345,219 US20170219077A1 (en) | 2011-09-06 | 2016-11-07 | Compact planetary differential gear set arrangement |
Related Parent Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/342,900 Division US9488265B2 (en) | 2011-09-06 | 2012-09-04 | Compact planetary differential gear set arrangement |
PCT/US2012/053672 Division WO2013036483A1 (en) | 2011-09-06 | 2012-09-04 | Compact planetary differential gear set arrangement |
Publications (1)
Publication Number | Publication Date |
---|---|
US20170219077A1 true US20170219077A1 (en) | 2017-08-03 |
Family
ID=46934694
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/342,900 Expired - Fee Related US9488265B2 (en) | 2011-09-06 | 2012-09-04 | Compact planetary differential gear set arrangement |
US15/345,219 Abandoned US20170219077A1 (en) | 2011-09-06 | 2016-11-07 | Compact planetary differential gear set arrangement |
Family Applications Before (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/342,900 Expired - Fee Related US9488265B2 (en) | 2011-09-06 | 2012-09-04 | Compact planetary differential gear set arrangement |
Country Status (4)
Country | Link |
---|---|
US (2) | US9488265B2 (en) |
EP (1) | EP2753849A1 (en) |
CN (2) | CN102979879B (en) |
WO (1) | WO2013036483A1 (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10167940B2 (en) * | 2015-10-07 | 2019-01-01 | Musashi Seimitsu Industry Co., Ltd. | Differential device |
DE102018220105A1 (en) * | 2018-11-22 | 2020-05-28 | Audi Ag | Differential gear for a motor vehicle |
KR20230095715A (en) | 2021-12-22 | 2023-06-29 | 삼보모터스주식회사 | Disserential Gear Device |
Families Citing this family (19)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2753849A1 (en) * | 2011-09-06 | 2014-07-16 | Eaton Corporation | Compact planetary differential gear set arrangement |
DE102013222731A1 (en) * | 2013-11-08 | 2015-05-13 | Schaeffler Technologies Gmbh & Co. Kg | Sliding sleeve for storing sun gears |
DE102013222831A1 (en) * | 2013-11-11 | 2015-05-13 | Schaeffler Technologies AG & Co. KG | Support arrangement for a lightweight building planetary differential |
CN103697138A (en) * | 2013-12-30 | 2014-04-02 | 郑州精益达汽车零部件有限公司 | Differential for passenger car |
DE102014000499B4 (en) * | 2014-01-16 | 2022-08-11 | Mercedes-Benz Group AG | Differential gear for a motor vehicle with at least one thin-walled carrier element in a lightweight construction |
DE102014213329A1 (en) * | 2014-07-09 | 2016-01-14 | Schaeffler Technologies AG & Co. KG | Planetary gear with cohesively connected housing structure |
CN104148797B (en) * | 2014-08-13 | 2016-07-06 | 江苏南铸科技股份有限公司 | The manufacture method of planetary wheel carrier |
JP6487664B2 (en) * | 2014-10-22 | 2019-03-20 | 武蔵精密工業株式会社 | Differential |
DE102015206132A1 (en) * | 2015-04-07 | 2016-10-13 | Schaeffler Technologies AG & Co. KG | Multi-part differential cage of a spur gear differential composed of forged and sheet metal parts |
CN108603580B (en) * | 2016-02-10 | 2021-11-23 | 麦格纳动力系美国有限公司 | Differential assembly with two-piece carrier and welded ring gear |
DE102016214015B4 (en) | 2016-07-29 | 2022-03-31 | Schaeffler Technologies AG & Co. KG | Planetary differential device and method of manufacturing the planetary differential device |
JP6847522B2 (en) * | 2017-02-22 | 2021-03-24 | ジヤトコ株式会社 | Joining method |
USD885450S1 (en) | 2017-05-15 | 2020-05-26 | Torq-Masters Industries, Inc | Vehicular differential replacement device |
US10167938B2 (en) | 2017-05-16 | 2019-01-01 | Schaeffler Technologies AG & Co. KG | Compact planetary differential |
JP6891659B2 (en) * | 2017-06-21 | 2021-06-18 | 株式会社ジェイテクト | Differential device |
USD848497S1 (en) * | 2017-09-14 | 2019-05-14 | Torq-Masters, Inc. | Axle gear |
US10731742B2 (en) | 2017-12-08 | 2020-08-04 | Torq-Masters Industries, Inc | Axle coupler with ring recess |
DE102019100374B4 (en) * | 2018-11-28 | 2021-07-22 | Schaeffler Technologies AG & Co. KG | Spur gear differential gear with coupling planets that differ by profile shifting |
USD906388S1 (en) | 2019-06-11 | 2020-12-29 | Torq-Masters Industries, Inc. | Automatic locking differential |
Family Cites Families (30)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB178201321A (en) | 1782-07-03 | 1782-07-04 | James Watt | |
GB800230A (en) | 1955-12-13 | 1958-08-20 | N S U Werke A G | Differential gearing for driving the wheels of motor vehicles |
US3433922A (en) * | 1964-08-10 | 1969-03-18 | Mech Tronics Corp | Electron beam welding machine |
JPH0674835B2 (en) | 1986-03-27 | 1994-09-21 | マテックス株式会社 | Casing mounting structure for planetary gear unit |
GB9100382D0 (en) | 1991-01-09 | 1991-02-20 | Lotus Group Plc | Differential unit |
US5239721A (en) * | 1991-07-17 | 1993-08-31 | Royal Appliance Mfg. Co. | Planetary gear system for sweeper brush roll |
US5433673A (en) * | 1993-05-06 | 1995-07-18 | Zexel Torsen Inc. | Differential with pivotable gear mountings |
JP4423716B2 (en) * | 1999-10-08 | 2010-03-03 | アイシン・エィ・ダブリュ株式会社 | Planetary carrier |
USD479542S1 (en) | 2002-05-02 | 2003-09-09 | Sew-Eurodrive Gmbh & Co. | Planetary gear with square flange |
DE102004015278A1 (en) | 2004-03-29 | 2005-10-20 | Josef Gail | Differential transmission for go-kart has each spur gear path with at least one central spur gear and at least one radially offset spur gear |
US20060160652A1 (en) * | 2005-01-14 | 2006-07-20 | Team Industries, Inc. | Spur gear differential |
EP1803973B1 (en) | 2005-12-27 | 2012-10-24 | ELASIS - Società Consortile per Azioni | Differential assembly provided with an adjustment device, in particular for motor vehicles |
GB0601716D0 (en) | 2006-01-27 | 2006-03-08 | Meritor Heavy Vehicle Sys Ltd | Differential gear casing and method |
DE102006019131B4 (en) | 2006-04-21 | 2008-01-24 | Getrag Driveline Systems Gmbh | Axisymmetrical, active axle drive |
DE102007004710B4 (en) | 2007-01-31 | 2012-09-27 | Schaeffler Technologies Gmbh & Co. Kg | Spur gear |
DE102007017185B4 (en) | 2007-04-12 | 2008-12-18 | Fzgmbh | Transfer case for motor vehicles |
JP5124232B2 (en) | 2007-10-25 | 2013-01-23 | 株式会社ジーテクト | Power transmission component and manufacturing method thereof |
JP5303970B2 (en) * | 2008-03-11 | 2013-10-02 | トヨタ自動車株式会社 | Carrier assembly |
JP5125761B2 (en) * | 2008-05-23 | 2013-01-23 | 株式会社ジェイテクト | Planetary carrier, planetary gear mechanism, and vehicle differential equipped with these |
US8388487B2 (en) | 2008-06-05 | 2013-03-05 | Jtekt Corporation | Differential apparatus for vehicle |
CN101649884B (en) | 2008-08-15 | 2013-11-13 | 德昌电机(深圳)有限公司 | Transmission structure and motor assembly with same |
DE102009032286B4 (en) | 2008-12-18 | 2022-01-05 | Schaeffler Technologies AG & Co. KG | Spur gear differential with positive and negative profile shift on the sun gears |
KR20100084294A (en) | 2009-01-16 | 2010-07-26 | 오문근 | Differential |
JP4785976B1 (en) | 2010-04-13 | 2011-10-05 | 川崎重工業株式会社 | Planetary gear set |
DE102010020414A1 (en) | 2010-05-12 | 2011-11-17 | Ims Gear Gmbh | Planetary gear with anti-rotation lock |
JP5411111B2 (en) | 2010-11-25 | 2014-02-12 | 川崎重工業株式会社 | Planetary gear reducer |
DE202011110376U1 (en) | 2011-01-03 | 2014-01-17 | Robert Bosch Gmbh | Planetary gear for a machine tool |
EP2753849A1 (en) * | 2011-09-06 | 2014-07-16 | Eaton Corporation | Compact planetary differential gear set arrangement |
US8900091B2 (en) | 2012-02-24 | 2014-12-02 | Nittan Valve Co., Ltd. | Planetary gear reduction mechanism |
USD720377S1 (en) | 2012-07-19 | 2014-12-30 | Eaton Corporation | Planetary differential gear set |
-
2012
- 2012-09-04 EP EP12766224.5A patent/EP2753849A1/en not_active Withdrawn
- 2012-09-04 US US14/342,900 patent/US9488265B2/en not_active Expired - Fee Related
- 2012-09-04 WO PCT/US2012/053672 patent/WO2013036483A1/en active Application Filing
- 2012-09-06 CN CN201210430469.XA patent/CN102979879B/en not_active Expired - Fee Related
- 2012-09-06 CN CN2012205709311U patent/CN203051679U/en not_active Expired - Fee Related
-
2016
- 2016-11-07 US US15/345,219 patent/US20170219077A1/en not_active Abandoned
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10167940B2 (en) * | 2015-10-07 | 2019-01-01 | Musashi Seimitsu Industry Co., Ltd. | Differential device |
DE102018220105A1 (en) * | 2018-11-22 | 2020-05-28 | Audi Ag | Differential gear for a motor vehicle |
DE102018220105B4 (en) * | 2018-11-22 | 2021-01-21 | Audi Ag | Differential gear for a motor vehicle with an output gear pressed onto the housing through two press fits |
US11353100B2 (en) | 2018-11-22 | 2022-06-07 | Audi Ag | Differential gear for a motor vehicle |
KR20230095715A (en) | 2021-12-22 | 2023-06-29 | 삼보모터스주식회사 | Disserential Gear Device |
Also Published As
Publication number | Publication date |
---|---|
WO2013036483A1 (en) | 2013-03-14 |
EP2753849A1 (en) | 2014-07-16 |
US9488265B2 (en) | 2016-11-08 |
US20140315677A1 (en) | 2014-10-23 |
CN102979879A (en) | 2013-03-20 |
CN203051679U (en) | 2013-07-10 |
CN102979879B (en) | 2017-04-12 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US20170219077A1 (en) | Compact planetary differential gear set arrangement | |
US8221278B2 (en) | Spur gear differential | |
US7695392B2 (en) | Differential mechanism assembly | |
US6061907A (en) | Method for making a differential mechanism for an automotive vehicle | |
US7901318B2 (en) | Four pinion differential with cross pin retention unit and related method | |
EP3144561B1 (en) | Bogie axle assembly | |
US20100105515A1 (en) | Planet pinion carrier for a gearset | |
US7524258B2 (en) | Vehicular automatic transmission | |
CN104220784A (en) | Combined sliding bearing in planetary gear train | |
US6379277B1 (en) | Limited slip differential mechanism for an automotive vehicle and method for making the same | |
US20160169360A1 (en) | Differential device | |
CN103133632A (en) | Spur gear differential and manufacturing method thereof | |
US9651132B2 (en) | Aluminum differential housing with cast iron inserts | |
CN1701983B (en) | Output yoke shaft and assembly | |
US20160116045A1 (en) | Differential device | |
CN103057406A (en) | Direct through type single-stage reduction drive axle | |
US10378613B1 (en) | Electric powertrain with cycloidal mechanism | |
JP2016080152A (en) | Differential gear | |
JP2015031313A (en) | Change gear | |
US11231099B2 (en) | Axle assembly and differential assembly with spider shaft retention | |
CN202965952U (en) | Directly through type single-stage reducing drive axle | |
JP2019074210A (en) | Drive module | |
US11225107B1 (en) | Axle carrier housing with reinforcement structure | |
US10865852B2 (en) | Powertrain with cycloidal mechanism having reinforced contact surfaces | |
US10948065B2 (en) | Differential device |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |