US20130231213A1 - Transmission with double-sun, annular gear, and outer gear coplanar gear set - Google Patents
Transmission with double-sun, annular gear, and outer gear coplanar gear set Download PDFInfo
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- US20130231213A1 US20130231213A1 US13/744,720 US201313744720A US2013231213A1 US 20130231213 A1 US20130231213 A1 US 20130231213A1 US 201313744720 A US201313744720 A US 201313744720A US 2013231213 A1 US2013231213 A1 US 2013231213A1
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- gear
- sun gear
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- 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
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
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- 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
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/70—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
Definitions
- the present teachings generally include transmissions that have a coplanar gear set.
- Most passenger vehicles include a powertrain that has an engine, a multi-speed transmission, and a differential or final drive.
- the multi-speed transmission increases the overall operating range of the vehicle by permitting the engine to operate through its torque range a number of times.
- a primary focus of transmission and engine design is increasing vehicle fuel efficiency. Generally, an increased number of speed ratios provides greater fuel efficiency.
- a transmission has a coplanar gear set with two sun gear members, an annular gear, a common carrier member, and an outer gear.
- the transmission includes a coplanar gear set having a first sun gear member rotatable about a first axis of rotation.
- the first sun gear member has a radially outward-facing surface defining outer teeth.
- the transmission has a second sun gear member rotatable about the first axis of rotation.
- the second sun gear member has a radially outward-facing surface defining outer teeth.
- the transmission has a carrier member.
- a first annular gear is supported by the carrier member and has a radially inward-facing surface defining inner teeth and a radially outward-facing surface defining outer teeth.
- the first annular gear is rotatable about a second axis of rotation that rotates about the first axis of rotation.
- the inner teeth of the first annular gear mesh with the outer teeth of the first sun gear member.
- An outer gear is supported by the carrier member and has a radially inward-facing surface defining inner teeth.
- the outer gear is rotatable about a third axis of rotation that rotates about the first axis of rotation.
- the inner teeth of the outer gear mesh with the outer teeth of the first annular gear and with the outer teeth of the second sun gear member.
- a coplanar gear set By providing the coplanar gear set with another gear set that may or may not also be a coplanar gear set, axial space savings are achieved. Moreover, a coplanar gear set can achieve a wider gear set ratio range than a planetary gear set, has a high contact ratio, and has relatively quiet operation.
- FIG. 1 is a schematic cross-sectional illustration of a portion of a first embodiment of a transmission including a coplanar gear set taken at lines 1 - 1 in FIG. 2 .
- FIG. 2 is a schematic cross-sectional illustration of the portion of the transmission of FIG. 1 taken at lines 2 - 2 in FIG. 1 .
- FIG. 3 is a schematic cross-sectional illustration of a portion of a second embodiment of a transmission including a coplanar gear set.
- FIGS. 1 and 2 show a portion of a transmission 10 that includes a coplanar gear set 12 .
- a “coplanar gear set” is a gear set that includes an annular gear.
- an “annular gear” is a gear that is generally cylindrical with radially inward-facing teeth (i.e., inner teeth) and radially outward-facing teeth (i.e., outer teeth) and has an axis of rotation that is offset from an axis of rotation of the gears with which it meshes.
- An annular gear may also be referred to herein as a cluster gear. The annular gear meshes both at its inner teeth and outer teeth with other members of the coplanar gear set or with a member of another gear set.
- the coplanar gear set 12 has a first sun gear member 16 rotatable about a first axis of rotation 18 .
- the first sun gear member 16 is mounted on and may be integrally formed with a center shaft 20 .
- the first sun gear member 16 has a radially outward-facing surface 14 defining outer teeth 17 .
- the coplanar gear set 12 has a second sun gear member 15 with a hub 23 having a central opening 19 that receives the shaft 20 so that the second sun gear member 15 is supported on the shaft 20 .
- the second sun gear member 15 has a radially outward-facing surface 21 that defines outer teeth 27 .
- the coplanar gear set 12 has a first annular gear 32 that has a radially inward-facing surface 34 with inner teeth 36 and a radially outward-facing surface 38 with outer teeth 40 .
- the coplanar gear set 12 also has a carrier member 42 .
- the carrier member 42 has an inner opening 43 at which it is rotatably supported by the shaft 20 . That is, the first carrier member 42 can rotate relative to the shaft 20 and the first sun gear member 16 .
- the carrier member 42 also has a generally cylindrical first hub 44 that is not centered with the first axis of rotation 18 . That is, the first hub 44 is an eccentric hub.
- the first annular gear 32 is supported by the first hub 44 of the carrier member 42 at a first set of cluster bearings 46 so that the first annular gear 32 is rotatable relative to the hub 44 . Because the hub 44 is not centered with the first axis of rotation 18 , the first annular gear 32 has a second axis of rotation 48 that is offset from the first axis of rotation 18 . Specifically, the first annular gear 32 will rotate around the second axis of rotation 48 , and as the first annular gear 32 moves the second axis of rotation 48 will rotate around the first axis of rotation 18 in a circle with a radius R 1 that is equal to the distance by which the second axis of rotation 48 is offset from the first axis of rotation 18 .
- the coplanar gear set 12 has an outer gear 56 that has a radially inward-facing surface 60 with inner teeth 62 .
- the outer gear 56 is a ring gear member because it has inner teeth 62 but no outer teeth.
- an alternative transmission 110 has a coplanar gear set 112 alike in all aspects and functionality as the coplanar gear set 12 except that an outer gear 156 used in place of outer gear 56 is an annular gear because it has both a radially inward-facing surface 60 with inner teeth 62 and a radially outward-facing surface 164 with outer teeth 166 .
- the carrier member 42 also has a generally cylindrical second hub 45 that is not centered with the first axis of rotation 18 . That is, the second hub 45 is an eccentric hub.
- the outer gear 56 is supported by the second hub 45 of the carrier member 42 at a second set of cluster bearings 58 so that the outer gear 56 is rotatable relative to the second hub 45 .
- the first hub 44 extends axially from the second hub 45 . Both the first annular gear 32 and the outer gear 56 are thus supported by a single, common carrier member 42 .
- the outer gear 56 has a third axis of rotation 68 that is offset from the first axis of rotation 18 . Specifically, the outer gear 56 will rotate around the third axis of rotation 68 , and as the outer gear 56 moves the third axis of rotation 68 will rotate around the first axis of rotation 18 in a circle with a radius R 2 that is equal to the distance by which the third axis of rotation 68 is offset from the first axis of rotation 18 .
- the inner teeth 36 of the first annular gear 32 mesh with the outer teeth 17 of the first sun gear member 16 .
- the outer teeth 40 of the first annular gear 32 mesh with the inner teeth 62 of the outer gear 56 .
- the outer teeth 27 of the second sun gear member 15 also mesh with the inner teeth 62 of the outer gear 56 .
- the hub 23 of the second sun gear member 15 is positioned so that the first sun gear member 16 is positioned axially between the hub 23 of the second sun gear member 15 and the carrier member 42 , and the first annular gear 32 is positioned axially between the second sun gear member 15 and the carrier member 42 .
- the second sun gear member 15 has a generally cylindrical recess 43 .
- the first sun gear member 16 and the first annular gear 32 are partially within the recess 43 so that a toothed portion 49 of the second sun gear member 15 radially surrounds the first sun gear member 16 and radially surrounds a portion 47 of the first annular gear 32 having the inner teeth 36 .
- the second sun gear member 15 is radially surrounded by the outer gear 56
- the first sun gear member 16 is radially surrounded by the first annular gear 32 , the second sun gear member 15 , and the outer gear 56 .
- a radial plane P perpendicular to the first axis of rotation 18 and placed through the coplanar gear set 12 intersects the first sun gear member 16 , the first annular gear 32 , the second sun gear member 15 , and the outer gear 56 , so that the meshing of the first sun gear member 16 with the first annular gear 32 , meshing of the first annular gear 32 with the outer gear 56 , and meshing of the second sun gear member 15 with the outer gear 56 all occur in the single radial plane P.
- the coplanar gear set 12 can be used within the transmission 10 along with one or more additional gear sets and various selectively engageable torque-transmitting mechanisms to provide multiple speed ratios in a relatively compact axial space. That is, the axial width occupied by the coplanar gear set 12 is less than the axial width that would be required for two axially-adjacent, simple planetary gear sets that may be necessary to provide the ratio range available with the coplanar gear set 12 , potentially reducing weight and increasing fuel economy. Axial space savings, wide gear set ratio range, high contact ratio, and quiet operation can also be achieved.
- w ag *C w og *D;
- w s1 is the rotational speed in revolutions per minute (rpm) of the first sun gear member 16 ;
- w s2 is the rotational speed in revolutions per minute (rpm) of the second sun gear member 15 ;
- w ag is the rotational speed in rpm of the first annular gear 32 ;
- w og is the rotational speed in rpm of the outer gear 56
- w c is the rotational speed in rpm of the carrier member 42 ;
- A is the number of teeth 17 of the first sun gear member 16 ;
- B is the number of inner teeth 36 of the first annular gear 32 ;
- C is the number of outer teeth 40 of the first annular gear 32 ;
- D is the number of inner teeth 62 of the outer gear 56 ;
- E is the number of outer teeth 27 of the second sun gear member 15 .
- Additional speed ratios can be established by adding either or both of one or more additional gear sets and one or more additional torque-transmitting mechanisms (i.e., clutches or brakes) to the transmission 10 or the transmission 110 .
- additional torque-transmitting mechanisms i.e., clutches or brakes
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Abstract
Description
- U.S. Provisional Application No. 61/606,125 filed on Mar. 2, 2012 is hereby incorporated by reference in its entirety.
- The present teachings generally include transmissions that have a coplanar gear set.
- Most passenger vehicles include a powertrain that has an engine, a multi-speed transmission, and a differential or final drive. The multi-speed transmission increases the overall operating range of the vehicle by permitting the engine to operate through its torque range a number of times. A primary focus of transmission and engine design is increasing vehicle fuel efficiency. Generally, an increased number of speed ratios provides greater fuel efficiency. However, it is challenging to package gear sets and selectively engageable torque-transmitting mechanisms to achieve the desired modes of operation while still meeting other applicable dimensional limitations and achieving relatively simple assembly requirements.
- A transmission is provided that has a coplanar gear set with two sun gear members, an annular gear, a common carrier member, and an outer gear. Specifically, the transmission includes a coplanar gear set having a first sun gear member rotatable about a first axis of rotation. The first sun gear member has a radially outward-facing surface defining outer teeth. The transmission has a second sun gear member rotatable about the first axis of rotation. The second sun gear member has a radially outward-facing surface defining outer teeth. The transmission has a carrier member. A first annular gear is supported by the carrier member and has a radially inward-facing surface defining inner teeth and a radially outward-facing surface defining outer teeth. The first annular gear is rotatable about a second axis of rotation that rotates about the first axis of rotation. The inner teeth of the first annular gear mesh with the outer teeth of the first sun gear member. An outer gear is supported by the carrier member and has a radially inward-facing surface defining inner teeth. The outer gear is rotatable about a third axis of rotation that rotates about the first axis of rotation. The inner teeth of the outer gear mesh with the outer teeth of the first annular gear and with the outer teeth of the second sun gear member.
- By providing the coplanar gear set with another gear set that may or may not also be a coplanar gear set, axial space savings are achieved. Moreover, a coplanar gear set can achieve a wider gear set ratio range than a planetary gear set, has a high contact ratio, and has relatively quiet operation.
- The above features and advantages and other features and advantages of the present invention are readily apparent from the following detailed description of the best modes for carrying out the invention when taken in connection with the accompanying drawings.
-
FIG. 1 is a schematic cross-sectional illustration of a portion of a first embodiment of a transmission including a coplanar gear set taken at lines 1-1 inFIG. 2 . -
FIG. 2 is a schematic cross-sectional illustration of the portion of the transmission ofFIG. 1 taken at lines 2-2 inFIG. 1 . -
FIG. 3 is a schematic cross-sectional illustration of a portion of a second embodiment of a transmission including a coplanar gear set. - Referring to the drawings, wherein like reference numbers refer to like components throughout the several views,
FIGS. 1 and 2 show a portion of atransmission 10 that includes acoplanar gear set 12. As used herein, a “coplanar gear set” is a gear set that includes an annular gear. As used herein, an “annular gear” is a gear that is generally cylindrical with radially inward-facing teeth (i.e., inner teeth) and radially outward-facing teeth (i.e., outer teeth) and has an axis of rotation that is offset from an axis of rotation of the gears with which it meshes. An annular gear may also be referred to herein as a cluster gear. The annular gear meshes both at its inner teeth and outer teeth with other members of the coplanar gear set or with a member of another gear set. - The
coplanar gear set 12 has a firstsun gear member 16 rotatable about a first axis ofrotation 18. The firstsun gear member 16 is mounted on and may be integrally formed with acenter shaft 20. The firstsun gear member 16 has a radially outward-facingsurface 14 definingouter teeth 17. - The
coplanar gear set 12 has a secondsun gear member 15 with ahub 23 having acentral opening 19 that receives theshaft 20 so that the secondsun gear member 15 is supported on theshaft 20. The secondsun gear member 15 has a radially outward-facingsurface 21 that definesouter teeth 27. - The
coplanar gear set 12 has a firstannular gear 32 that has a radially inward-facingsurface 34 withinner teeth 36 and a radially outward-facingsurface 38 withouter teeth 40. Thecoplanar gear set 12 also has acarrier member 42. Thecarrier member 42 has aninner opening 43 at which it is rotatably supported by theshaft 20. That is, thefirst carrier member 42 can rotate relative to theshaft 20 and the firstsun gear member 16. Thecarrier member 42 also has a generally cylindricalfirst hub 44 that is not centered with the first axis ofrotation 18. That is, thefirst hub 44 is an eccentric hub. The firstannular gear 32 is supported by thefirst hub 44 of thecarrier member 42 at a first set ofcluster bearings 46 so that the firstannular gear 32 is rotatable relative to thehub 44. Because thehub 44 is not centered with the first axis ofrotation 18, the firstannular gear 32 has a second axis ofrotation 48 that is offset from the first axis ofrotation 18. Specifically, the firstannular gear 32 will rotate around the second axis ofrotation 48, and as the firstannular gear 32 moves the second axis ofrotation 48 will rotate around the first axis ofrotation 18 in a circle with a radius R1 that is equal to the distance by which the second axis ofrotation 48 is offset from the first axis ofrotation 18. - The
coplanar gear set 12 has anouter gear 56 that has a radially inward-facingsurface 60 withinner teeth 62. In the embodiment shown, theouter gear 56 is a ring gear member because it hasinner teeth 62 but no outer teeth. Alternatively, as shown inFIG. 3 , analternative transmission 110 has acoplanar gear set 112 alike in all aspects and functionality as the coplanar gear set 12 except that anouter gear 156 used in place ofouter gear 56 is an annular gear because it has both a radially inward-facingsurface 60 withinner teeth 62 and a radially outward-facingsurface 164 withouter teeth 166. - The
carrier member 42 also has a generally cylindricalsecond hub 45 that is not centered with the first axis ofrotation 18. That is, thesecond hub 45 is an eccentric hub. Theouter gear 56 is supported by thesecond hub 45 of thecarrier member 42 at a second set ofcluster bearings 58 so that theouter gear 56 is rotatable relative to thesecond hub 45. As is apparent inFIG. 2 , thefirst hub 44 extends axially from thesecond hub 45. Both the firstannular gear 32 and theouter gear 56 are thus supported by a single,common carrier member 42. Because thesecond hub 45 is not centered with the first axis ofrotation 18 or with the second axis ofrotation 48, theouter gear 56 has a third axis ofrotation 68 that is offset from the first axis ofrotation 18. Specifically, theouter gear 56 will rotate around the third axis ofrotation 68, and as theouter gear 56 moves the third axis ofrotation 68 will rotate around the first axis ofrotation 18 in a circle with a radius R2 that is equal to the distance by which the third axis ofrotation 68 is offset from the first axis ofrotation 18. - The
inner teeth 36 of the firstannular gear 32 mesh with theouter teeth 17 of the firstsun gear member 16. Theouter teeth 40 of the firstannular gear 32 mesh with theinner teeth 62 of theouter gear 56. Theouter teeth 27 of the secondsun gear member 15 also mesh with theinner teeth 62 of theouter gear 56. Thehub 23 of the secondsun gear member 15 is positioned so that the firstsun gear member 16 is positioned axially between thehub 23 of the secondsun gear member 15 and thecarrier member 42, and the firstannular gear 32 is positioned axially between the secondsun gear member 15 and thecarrier member 42. The secondsun gear member 15 has a generallycylindrical recess 43. The firstsun gear member 16 and the firstannular gear 32 are partially within therecess 43 so that atoothed portion 49 of the secondsun gear member 15 radially surrounds the firstsun gear member 16 and radially surrounds aportion 47 of the firstannular gear 32 having theinner teeth 36. - The second
sun gear member 15 is radially surrounded by theouter gear 56, and the firstsun gear member 16 is radially surrounded by the firstannular gear 32, the secondsun gear member 15, and theouter gear 56. - As is apparent in
FIG. 2 , a radial plane P perpendicular to the first axis ofrotation 18 and placed through the coplanar gear set 12 intersects the firstsun gear member 16, the firstannular gear 32, the secondsun gear member 15, and theouter gear 56, so that the meshing of the firstsun gear member 16 with the firstannular gear 32, meshing of the firstannular gear 32 with theouter gear 56, and meshing of the secondsun gear member 15 with theouter gear 56 all occur in the single radial plane P. - The coplanar gear set 12 can be used within the
transmission 10 along with one or more additional gear sets and various selectively engageable torque-transmitting mechanisms to provide multiple speed ratios in a relatively compact axial space. That is, the axial width occupied by the coplanar gear set 12 is less than the axial width that would be required for two axially-adjacent, simple planetary gear sets that may be necessary to provide the ratio range available with the coplanar gear set 12, potentially reducing weight and increasing fuel economy. Axial space savings, wide gear set ratio range, high contact ratio, and quiet operation can also be achieved. - The speed relationships between the members of the coplanar gear set 12 are as follows:
-
w s1 *A=w ag *B+w c *A; -
w s2 *E=w og *D+w c *E; and - wag*C=wog*D; where ws1 is the rotational speed in revolutions per minute (rpm) of the first
sun gear member 16; ws2 is the rotational speed in revolutions per minute (rpm) of the secondsun gear member 15; wag is the rotational speed in rpm of the firstannular gear 32; wog is the rotational speed in rpm of theouter gear 56, wc is the rotational speed in rpm of thecarrier member 42; A is the number ofteeth 17 of the firstsun gear member 16; B is the number ofinner teeth 36 of the firstannular gear 32; C is the number ofouter teeth 40 of the firstannular gear 32; D is the number ofinner teeth 62 of theouter gear 56; and E is the number ofouter teeth 27 of the secondsun gear member 15. Simplifying the relationship provides: - ws1*A−ws2*E=wag*(B−C)+wc*(A−E). The same relationships apply to the coplanar gear set 112 of
FIG. 3 , with wog being the speed in rpm of theannular gear 156 and D being the number ofinner teeth 62 of theouter gear 156. - Additional speed ratios can be established by adding either or both of one or more additional gear sets and one or more additional torque-transmitting mechanisms (i.e., clutches or brakes) to the
transmission 10 or thetransmission 110. - While the best modes for carrying out the invention have been described in detail, those familiar with the art to which this invention relates will recognize various alternative designs and embodiments for practicing the invention within the scope of the appended claims.
Claims (15)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
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US13/744,720 US8529392B1 (en) | 2012-03-02 | 2013-01-18 | Transmission with double-sun, annular gear, and outer gear coplanar gear set |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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US201261606125P | 2012-03-02 | 2012-03-02 | |
US13/744,720 US8529392B1 (en) | 2012-03-02 | 2013-01-18 | Transmission with double-sun, annular gear, and outer gear coplanar gear set |
Publications (2)
Publication Number | Publication Date |
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US20130231213A1 true US20130231213A1 (en) | 2013-09-05 |
US8529392B1 US8529392B1 (en) | 2013-09-10 |
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Family Applications (4)
Application Number | Title | Priority Date | Filing Date |
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US13/744,712 Active US8758183B2 (en) | 2012-03-02 | 2013-01-18 | Transmission with double-sun, one ring, and double-annular gear coplanar gear set |
US13/744,706 Expired - Fee Related US8936527B2 (en) | 2012-03-02 | 2013-01-18 | Transmission with radially stacked gear sets including annular gear |
US13/744,720 Expired - Fee Related US8529392B1 (en) | 2012-03-02 | 2013-01-18 | Transmission with double-sun, annular gear, and outer gear coplanar gear set |
US13/744,727 Expired - Fee Related US8585527B2 (en) | 2012-03-02 | 2013-01-18 | Transmission with double-annular gear coplanar gear set |
Family Applications Before (2)
Application Number | Title | Priority Date | Filing Date |
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US13/744,712 Active US8758183B2 (en) | 2012-03-02 | 2013-01-18 | Transmission with double-sun, one ring, and double-annular gear coplanar gear set |
US13/744,706 Expired - Fee Related US8936527B2 (en) | 2012-03-02 | 2013-01-18 | Transmission with radially stacked gear sets including annular gear |
Family Applications After (1)
Application Number | Title | Priority Date | Filing Date |
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US13/744,727 Expired - Fee Related US8585527B2 (en) | 2012-03-02 | 2013-01-18 | Transmission with double-annular gear coplanar gear set |
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Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20130231211A1 (en) * | 2012-03-02 | 2013-09-05 | GM Global Technology Operations LLC | Transmission with radially stacked gear sets including annular gear |
CN106030152A (en) * | 2013-10-10 | 2016-10-12 | 澳商安博科技工业有限公司 | Rotary gear transmission for tools |
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DE102013015843A1 (en) * | 2013-09-24 | 2015-04-09 | Iwis Motorsysteme Gmbh & Co. Kg | Swash body gear |
TWI608186B (en) * | 2016-12-14 | 2017-12-11 | 財團法人工業技術研究院 | Transmitting device for wheel and power assist wheel set |
KR102585748B1 (en) * | 2018-06-28 | 2023-10-11 | 현대자동차주식회사 | Transmission of vehicle |
CN110953308B (en) * | 2020-01-11 | 2020-10-02 | 大连碧蓝节能环保科技有限公司 | Gear ring eccentric rotation stepless speed change method |
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US627383A (en) * | 1899-06-20 | birrell | ||
US733600A (en) * | 1903-03-24 | 1903-07-14 | Joseph Schneible | Power-transmitting device. |
US1123396A (en) * | 1910-10-17 | 1915-01-05 | Elmer Schoonmaker | Mechanical movement. |
US1124783A (en) * | 1912-10-11 | 1915-01-12 | Charles Josselyn Lay Moore | Variable-speed gearing. |
US1092438A (en) * | 1913-02-21 | 1914-04-07 | Rudolph A Wittemann | Speed-changing-gear mechanism. |
US1449351A (en) * | 1920-11-06 | 1923-03-20 | Ferdinand W Seeck | Steering gear |
US1715778A (en) * | 1927-03-26 | 1929-06-04 | Francis L Orr | Variable-speed transmission |
US1885156A (en) * | 1931-04-03 | 1932-11-01 | Reo Motor Car Co | Transmission mechanism |
US2214001A (en) * | 1934-10-24 | 1940-09-10 | Sneed John | Automatic transmission |
US2250259A (en) * | 1940-03-11 | 1941-07-22 | Jr Bradford Foote | Speed reducing gearing |
US2972910A (en) * | 1958-06-06 | 1961-02-28 | Abury H Temple | Speed reducer |
US3037400A (en) * | 1959-01-14 | 1962-06-05 | Edward V Sundt | Differential gear reducer |
US3145585A (en) * | 1962-10-18 | 1964-08-25 | Brown Brockmeyer Company | Epi-cycle gear train for floor polisher motor |
US3424318A (en) * | 1966-10-31 | 1969-01-28 | Lorence Mfg Corp | Turntable drive mechanism |
US3534636A (en) * | 1968-04-12 | 1970-10-20 | Lorence Mfg Corp | Speed reducing transmission |
US3729276A (en) * | 1971-07-06 | 1973-04-24 | Bendix Corp | Actuator assembly |
US4155276A (en) * | 1977-03-28 | 1979-05-22 | Fengler Werner H | High-ratio speed-reduction transmission |
US4282777A (en) * | 1979-01-02 | 1981-08-11 | Compudrive Corporation | Pancake planetary drive |
US4762025A (en) * | 1986-07-31 | 1988-08-09 | Lew Hyok S | All orbiting gear planetary drive |
CA2641075C (en) | 1997-11-03 | 2009-11-24 | Ker-Train Holdings Ltd. | Coplanar reverted gear train loop |
DE102004043310B4 (en) * | 2003-11-28 | 2009-08-06 | C. Rob. Hammerstein Gmbh & Co. Kg | Reduction gear for an adjustment of a motor vehicle seat |
DE102008000428A1 (en) | 2008-02-28 | 2009-09-03 | Zf Friedrichshafen Ag | Multi-speed transmission |
DE102008000429A1 (en) | 2008-02-28 | 2009-09-03 | Zf Friedrichshafen Ag | Multi-speed transmission |
US8016714B2 (en) | 2008-08-19 | 2011-09-13 | Ford Global Technologies, Llc | Multiple speed transmission utilizing co-planar gear sets |
US8758183B2 (en) * | 2012-03-02 | 2014-06-24 | GM Global Technology Operations LLC | Transmission with double-sun, one ring, and double-annular gear coplanar gear set |
-
2013
- 2013-01-18 US US13/744,712 patent/US8758183B2/en active Active
- 2013-01-18 US US13/744,706 patent/US8936527B2/en not_active Expired - Fee Related
- 2013-01-18 US US13/744,720 patent/US8529392B1/en not_active Expired - Fee Related
- 2013-01-18 US US13/744,727 patent/US8585527B2/en not_active Expired - Fee Related
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20130231211A1 (en) * | 2012-03-02 | 2013-09-05 | GM Global Technology Operations LLC | Transmission with radially stacked gear sets including annular gear |
US8936527B2 (en) * | 2012-03-02 | 2015-01-20 | GM Global Technology Operations LLC | Transmission with radially stacked gear sets including annular gear |
CN106030152A (en) * | 2013-10-10 | 2016-10-12 | 澳商安博科技工业有限公司 | Rotary gear transmission for tools |
Also Published As
Publication number | Publication date |
---|---|
US8585527B2 (en) | 2013-11-19 |
US8529392B1 (en) | 2013-09-10 |
US20130231211A1 (en) | 2013-09-05 |
US20130231214A1 (en) | 2013-09-05 |
US20130231212A1 (en) | 2013-09-05 |
US8758183B2 (en) | 2014-06-24 |
US8936527B2 (en) | 2015-01-20 |
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