WO2006046356A1 - プラネタリギア装置 - Google Patents
プラネタリギア装置 Download PDFInfo
- Publication number
- WO2006046356A1 WO2006046356A1 PCT/JP2005/016462 JP2005016462W WO2006046356A1 WO 2006046356 A1 WO2006046356 A1 WO 2006046356A1 JP 2005016462 W JP2005016462 W JP 2005016462W WO 2006046356 A1 WO2006046356 A1 WO 2006046356A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- pinion
- carrier
- planetary gear
- gear device
- short
- Prior art date
Links
- 230000002093 peripheral effect Effects 0.000 claims abstract description 20
- 238000003466 welding Methods 0.000 claims description 19
- 239000000523 sample Substances 0.000 claims description 4
- 238000000034 method Methods 0.000 claims description 3
- 241000920340 Pion Species 0.000 claims description 2
- 230000005540 biological transmission Effects 0.000 description 7
- 230000004323 axial length Effects 0.000 description 3
- 239000000470 constituent Substances 0.000 description 3
- 239000000463 material Substances 0.000 description 3
- MUXFZBHBYYYLTH-UHFFFAOYSA-N Zaltoprofen Chemical compound O=C1CC2=CC(C(C(O)=O)C)=CC=C2SC2=CC=CC=C21 MUXFZBHBYYYLTH-UHFFFAOYSA-N 0.000 description 1
- 239000012050 conventional carrier Substances 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005304 joining Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000013011 mating Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/08—General details of gearing of gearings with members having orbital motion
- F16H57/082—Planet carriers
-
- 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
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
- F16H3/663—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with conveying rotary motion between axially spaced orbital gears, e.g. RAVIGNEAUX
Definitions
- the present invention relates to a planetary gear device used for an automatic transmission or the like, and more particularly to improvement of a carrier in a double beon type planetary gear device having a short pinion and a tongue pinion.
- a double pinion type planetary gear device called a Ravigneo type is used in an automatic transmission of an automobile.
- a planetary gear device includes first and second sun gears supported on an input shaft so as to be relatively rotatable, as described in Japanese Patent Application Laid-Open No. Hei 10-1 6 9 7 28.
- the conventional carrier 100 used in such a double-pione type planetary gear device supports the short-pion 100 1 and the mouth pinion 100 2 so as to be rotatable.
- the first carrier body 10 6 having a bottomed cylindrical shape with a flange portion 10 5 supporting each end of the support shafts 10 3 and 10 4, and the flange portion of the first carrier 1 0 6 1 0 5 is spaced apart by a predetermined distance in the axial direction, and the support shaft 1 0 3, 1 0 4 is composed of two members, a second carrier body 10 8 having a flange portion 10 7 for supporting the other ends of the four.
- the flange portion 107 of the second carrier body 108 is formed on the flange portion 105 of the first carrier body 106 by a plurality of circumferentially extending bridge portions 1009 extending in the axial direction. Engaged with the ply connecting portion 110 and integrally joined by welding W0.
- the pinion size is determined by the restrictions of the gear ratio and needle capacity, so that the bridge portion 1 0 9 of the second carrier body 10 8 Thickness in the radial direction is increased because the axial length is long, and the bridge portion 10 09 in the box structure cannot be used due to the presence of the long pinion 10 0 2 and the radial space is limited. There is a restriction that cannot be increased.
- the circumferential space for passing the bridge portion 1 0 9 is also restricted. It becomes more difficult to secure sufficient strength of the bridge portion 10 9, and the torsional rigidity of the carrier 100 may be reduced.
- the carrier 100 that supports the short pinion 1001 and the lip pinion 1002 includes The torsional moment due to the counter reaction force acts. Therefore, if the rigidity of the carrier 100 is insufficient, the carrier 100 will be deformed and gears will not be properly meshed, resulting in problems such as a reduction in gear durability and the occurrence of gear noise. There is a fear.
- the present invention has been made in view of such problems, and an object of the present invention is to provide a planetary gear device with increased carrier rigidity.
- first and second sun gears supported so as to be relatively rotatable, a plurality of short beons on the circumference meshing with the first sun gear, the second sun gear and the short pieon, respectively.
- a double pinion type planetary gear device comprising a plurality of long pinions on the circumference that mesh with each other, a ring gear that meshes with the long pinion, and a carrier that rotatably supports the short pinion and the long pinion, respectively. And at least a first flange portion that supports one end of each of the short pinion and the long pinion, and a double pinion portion that is connected to the first flange portion and the short pinion and the long pinion are combined.
- a cylindrical portion that covers the entire outer periphery of the long pieon, and the other end of the long pieon And a plurality of pegs extending from the second flange toward the short pinion and supporting the other end of the short pinion. is there.
- the cylindrical portion that covers the entire outer periphery of the double pieon portion connected to the first flange portion and the short pinion and the long pinion are combined, and the short binion from the second flange portion. Since the box structure is configured by a plurality of pegs extending toward the front, the axial length of each bridge can be shortened, and the surroundings of the short pieon can be reduced as in the past. Since it is not necessary to pass through a limited space, a sufficient cross-sectional area can be ensured, and the torsional rigidity of the bridge portion and thus the torsional rigidity of the carrier can be greatly increased.
- the first carrier body including the first flange portion and the cylindrical portion, the second flange portion, and the plurality of probe portions are included.
- a second carrier body, and the cylindrical portion and the plurality of pledge portions are annular projections. It joins through a part, It is characterized by the above-mentioned.
- each component of the carrier can be mainly formed by press working, and the processing cost can be reduced.
- the annular protrusion extends from the inner diameter side of the ring gear toward the inner diameter side, and has a plurality of angles on the circumference corresponding to the long pinion It is characterized by having an arc-shaped notch at the position.
- the annular protrusion has an arc-shaped cutout at an angular position at a plurality of positions on the circumference corresponding to the long pinion, extending from the inner diameter side of the ring gear to the inner diameter side. Therefore, the increase in the diameter of the carrier can be suppressed as much as possible, and it can contribute to the miniaturization of the entire apparatus.
- the cylindrical portion and the annular protrusion, and the annular protrusion and the plurality of bridge portions are joined by welding, respectively,
- the welding of the annular projecting portion and the plurality of bridge portions is performed through a window formed in the first flange portion corresponding to the plurality of bridge portions.
- the welding of the annular protrusion and the plurality of pledges is performed through the window formed in the first flange corresponding to the plurality of the bridges.
- the inside of the carrier can be easily welded.
- a fifth invention is the planetary gear device according to the fourth invention, wherein The cylindrical portion and the annular protrusion, and the annular protrusion and the plurality of bridge portions are each joined by welding from one direction.
- a sixth invention is characterized in that, in the planetary gear device according to the first or second invention, a spline groove is provided on the outer peripheral surface of the cylindrical portion to allow a friction plate to be disposed. is there.
- the hap portion can be shared with the carrier member.
- the structure of the clutch mechanism or brake mechanism can be simplified and the size can be reduced.
- the annular projection has a hub portion extending in the axial direction on the outer peripheral side thereof, and the outer periphery of the hub portion.
- a spline groove that allows a friction plate to be disposed on the surface is formed.
- the spline groove that allows the friction plate to be disposed on the outer peripheral surface of the hub portion provided on the outer peripheral side of the annular projecting portion is configured. Therefore, the clutch mechanism in the automatic transmission or Since the structure of the brake mechanism can be formed, it can be connected to a predetermined rotating element of the carrier and the automatic transmission, or can be locked to the case.
- FIG. 1 is a sectional view of a double pinion type planetary gear device showing an embodiment of the present invention.
- Fig. 2 is cut along line A-A in Fig. 1.
- FIG. 3 is a cross-sectional view taken along line BB in FIG.
- FIG. 4 is a cross-sectional view taken along the line CC in FIG.
- FIG. 5 is an exploded view of the carrier in the embodiment of the present invention.
- FIG. 6 is a perspective view showing the carrier assembling sequence in FIG.
- FIG. 7 is a sectional view showing an example of a carrier of a conventional double beon type planetary gear device.
- FIG. 1 shows the entire double-ion type planetary gear device 10 in which two sets of planetary gears 1 1 and 1 2 are combined.
- FIG. 2, FIG. 3 and FIG. Fig. 2 shows cross-sections taken along lines A-A, B-B and C-C in Fig. 1, respectively.
- the planetary gear device 10 mainly includes an input shaft 13 that is rotatably supported by a case (not shown), and first and second sun gears 15 that are rotatably supported on the input shaft 13, respectively.
- the input shaft 13 is rotationally driven by an unillustrated engine, and a first hollow shaft 23 formed integrally with the first sun gear 15 is rotatably supported on the input shaft 13. Has been.
- a second hollow shaft 24 integrally formed with the second sun gear 16 is rotatably supported on the first hollow shaft 23.
- the first sun gear 15 and the second sun gear 16 are arranged side by side in the axial direction.
- the second sun gear 16 is formed to have a slightly larger diameter than the first sun gear 15.
- the carrier 20 has four short pinion shafts 25 supported at equal angular intervals at both ends, and the short pinion shafts 25 are rotatably supported by the short pinion shafts 25, respectively.
- the short pinion 17 is engaged with the first sun gear 15.
- the carrier 20 has four long pinion shafts 26 supported at equal circumferential intervals at both ends, and the long pinion shafts 26 are rotatably supported by the long pinion shafts 26, respectively.
- the second sun gear 16 and the ring gear 19 are combined with the right half of the long pinion 18 in FIG. 1, and the short pinion 17 is combined with the left half.
- the carrier 20 is shown as an example of three constituent members (pieces) so that it can be mainly formed by press working. That is, the carrier 20 includes the short pinion shaft 25 and the long pinion shaft.
- the first carrier body 3 2 includes a carrier member 35 having the first flange portion 31 and a hub member having an annular projection portion 36 which will be described later.
- the carrier 20 composed of three pieces is composed of the carrier member 3 5 and the hub member 3 7 of the first carrier body 32. Are joined together by welding W 1 as will be described later, and the annular projection 36 of the hap member 37 and the second carrier body 34 are joined together by welding W 2 as will be described later. Constructs the carrier 20 of the structure.
- the carrier member 35 constituting the first carrier body 32 has a bottomed cylindrical shape in which the outer peripheral portion of the disc-shaped first flange portion 31 is bent in the axial direction, and the cylindrical portion 4 1 extends almost to the center of the long pinion 18 in the axial direction, and covers the entire outer periphery of the double pinion portion where the short pinion 17 and the mouth dabion 1 8 are mated. Yes.
- a joint portion 42 that slightly bends radially outward is formed at the tip of the cylindrical portion 41.
- a first spline portion 43 is formed on the outer periphery of the cylindrical portion 41, and a multi-plate clutch mechanism 44 is connected to the first spline portion 43.
- the cylindrical portion 41 of the carrier member 35 constitutes the clutch hub of the multi-plate type clutch mechanism 44.
- the first spline portion 43 is omitted to simplify the drawing.
- the first flange portion 31 of the carrier member 35 has four shaft holes 4 on the circumference that support the shaft end of the long pinion shaft 26. 5 are formed at equiangular intervals, and four shaft holes 46 on the circumference supporting the shaft end of the short pinion shaft 25 are formed at equiangular intervals between the four shaft holes 45. .
- arcuate windows 47 are formed on the circumference at a plurality of locations (four locations in the embodiment), and these windows 47 are composed of the short pieon 17 and the carrier member. It is opened in a space between 3 and 5 cylindrical part 4 1.
- a hap member 37 that constitutes a part of the first carrier body 32 has a cylindrical hub portion 48 that surrounds the ring gear 19, and the cylindrical hub portion 48 is an annular protrusion 3. On the outer peripheral side of 6, it extends in the axial direction.
- Circle A second spline portion 49 having a diameter larger than that of the first spline portion 43 is formed on the outer periphery of the cylindrical hap portion 48, and a multi-plate type brake mechanism 50 is provided on the second spline portion 49. It is connected.
- the cylindrical hap part 48 of the hub member 37 constitutes a brake hub of the multi-plate brake mechanism 50.
- the second spline part 49 is also omitted as in the case of the first spline part 43.
- annular projection portion 36 that projects inward in the radial direction is formed.
- This projection portion 36 is formed of the long pinion 18 And extends to a side position of the ring gear 19.
- the inner diameter of the annular protrusion 36 extends from the inner diameter of the ring gear 19 that meshes with the long pinion 18 to the inner diameter side, and is on the circumference corresponding to the long pinion 18.
- arc-shaped notches 53 are formed at the four angular positions.
- the annular protrusion 36 is connected to the inner peripheral surface 5 1 centered on the axis of the input shaft 13 and at a right angle to the inner peripheral surface 51.
- the joint part which consists of end face 52 is formed.
- the outer peripheral surface of the joint portion 42 of the carrier member 35 is fitted to the inner peripheral surface 51, and the side surface of the joint portion 42 is brought into contact with the end surface 52. Both are integrally joined.
- Such welding W 1 is performed from the left side of FIG. 1 and FIG.
- the second carrier body 34 is directed to the side of each short pinion 17 from the end face of the disk-like second flange portion 33.
- a plurality of (four in the embodiment) bridge portions 55 provided on the circumference are provided.
- the 2nd flange 3 3 of the 2nd carrier body 3 4 has a circumference that supports the shaft end of the long pinion shaft 26.
- the upper four shaft holes 56 are formed at equiangular intervals, and the bridge portion 55 located between each of the four shaft holes 56 is provided on the circumference supporting the shaft end of the short pinion shaft 25.
- Four shaft holes 5 7 are formed at equiangular intervals.
- an arc surface 5 8 centering on the axis of the input shaft 1 3 and an end surface connected to the arc surface 5 8 at a right angle are provided at the tip of each bridge portion 5 5.
- a joint consisting of 5 9 is formed.
- the inner surface of the annular protrusion 36 is fitted to the circular arc surface 58, and the side surface of the protrusion 36 is brought into contact with the end surface 59. In this state, the two are integrally joined by welding W2.
- the cylindrical portion 41 of the first carrier body 32 and the plurality of pledge portions 55 of the second carrier body 34 are joined to each other via the annular protrusion 36.
- the weld W 2 passes through the first flange portion 31 of the carrier member 35 through a plurality of arc-shaped windows 4 7 opened corresponding to the plurality of bridge portions 55 to the left of FIG. 1 and FIG. It is executed at four places on the circumference.
- shaft holes 4 5 and 5 7 for fitting and supporting the short pinion shaft 25 and the mouth pinion shaft 26 are present in the same phase. It is shown.
- the planetary gear device 10 having the above-described configuration is assembled as follows. First, the carrier member 35 and hub member 37 of the first carrier body 32 and the three members of the second carrier body 34 are joined together to form a carrier 20 having a box structure.
- the annular protrusion 3 6 of the hap member 3 7 of the first carrier body 3 2 Of the second carrier body 3 4 is inlay-fitted to an arc surface 5 8 formed at the tip of each bridge portion 5 5, and the side surface is brought into contact with the end surface 59,
- the outer periphery of the joining portion 4 2 of the first carrier body 3 2 and the carrier member 3 5 is fitted into the inner peripheral surface 51 of the annular projection 3 6 of the hub member 37 and the side surface thereof is It abuts on the end face 52.
- the annular protrusions 36 of the carrier member 35 and the hub member 37 are joined together by welding W1 to form the first carrier body 32, and the annular protrusions are formed by welding W2.
- the second carrier body 3 4 is joined to 3 6.
- Such welding W 2 is performed through an arcuate window 47 opened in the first flange portion 31 of the carrier member 35.
- Each ply portion 55 of the carrier 20 has a double beon portion in which a short pinion 17 and a mouth pion 18 are combined. Is joined to the cylindrical part 41 covering the entire outer periphery of the outer peripheral side via the annular projection part 36, so that the axial length of the bridge part 55 can be shortened, and as in the conventional case. Since there is no need to pass through the limited space around the short peon 17, there is no restriction to reduce the thickness in the radial direction, sufficient cross-sectional area can be secured, and torsional rigidity can be greatly increased. .
- the carrier 20 can be assembled in a single welding process.
- the planetary gear device 10 is assembled, and the planetary gear device 10 is configured such that the first hollow shaft 23 of the first sun gear 15 is fitted and supported by the input shaft 13 and the carrier 20
- the clutch plates of the clutch mechanism 44 and the brake mechanism 50 are engaged with the first and second spline parts 4 3 and 4 9 and assembled to the automatic transmission.
- the present invention is not limited to this, and two sets of planetary gears 11 and 12 are provided. As long as it is equipped with a combined double-ion type planetary gear device 10, it can be applied to any device.
- the double pinion type planetary gear device 10 in which four short pinions 17 and four tongue pinions 18 are arranged on the circumference has been described, but the present invention is not necessarily limited to that.
- the number is not limited, for example, it can be applied to a planetary gear device in which three short pinions and three long pinions are arranged on the circumference, and can be appropriately selected according to the required capacity of the planetary gear device. is there.
- the carrier 20 is configured by three-piece constituent members.
- the three-piece configuration can form each constituent member mainly by press working, thereby reducing the production cost. It can be reduced, or it is effective in setting the optimum material according to the function of each part
- the annular protrusion 36 formed on the hap member 37 that constitutes a part of the first carrier body 32 is formed on the carrier member 35 side so that the first It is also possible to form the carrier 20 with two members, the first carrier body 3 2 and the second carrier body 3 4.
- the carrier 20 is composed of four or more components for the purpose of improving workability and material variations.
- the example in which the first and second sun gears 15 and 16 are supported on the input shaft 13 has been described.
- the present invention is not limited to such a configuration.
- a friction plate that forms a clutch or a brake on the outer peripheral side of the cylindrical portion 41 and the cylindrical hub portion 48 of the carrier 20 using the carrier 20 box structure.
- the planetary gear device according to the present invention is suitable for use in an automatic transmission that shifts and outputs the rotation of an automobile engine.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Details Of Gearings (AREA)
- Structure Of Transmissions (AREA)
- Retarders (AREA)
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112005001867T DE112005001867B4 (de) | 2004-10-26 | 2005-09-01 | Planetengetriebeeinheit |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2004310552A JP4715161B2 (ja) | 2004-10-26 | 2004-10-26 | プラネタリギヤ装置 |
JP2004-310552 | 2004-10-26 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2006046356A1 true WO2006046356A1 (ja) | 2006-05-04 |
Family
ID=36206847
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2005/016462 WO2006046356A1 (ja) | 2004-10-26 | 2005-09-01 | プラネタリギア装置 |
Country Status (5)
Country | Link |
---|---|
US (1) | US7316629B2 (ja) |
JP (1) | JP4715161B2 (ja) |
CN (1) | CN100451386C (ja) |
DE (1) | DE112005001867B4 (ja) |
WO (1) | WO2006046356A1 (ja) |
Families Citing this family (26)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20050188521A1 (en) * | 2004-02-26 | 2005-09-01 | Bernard Simon | Method for axial assembly of ravigneaux gearset |
JP4910606B2 (ja) * | 2006-09-29 | 2012-04-04 | アイシン・エィ・ダブリュ株式会社 | プラネタリギヤ装置 |
US7654929B2 (en) * | 2007-02-02 | 2010-02-02 | Ford Global Technologies, Llc | Assembly including a planetary pinion carrier and one-way clutch |
KR100983469B1 (ko) * | 2008-06-27 | 2010-09-24 | 현대 파워텍 주식회사 | 자동변속기용 유성기어장치 |
DE102008040123A1 (de) * | 2008-07-03 | 2010-01-07 | Zf Friedrichshafen Ag | Getriebevorrichtung mit wenigstens einem Planetenradsatz und einem reibschlüssigen Schaltelement |
JP4854720B2 (ja) * | 2008-09-24 | 2012-01-18 | 正博 大窪 | 複合遊星歯車を用いた多段自動変速機 |
DE102009042585A1 (de) * | 2008-12-15 | 2010-06-17 | Sew-Eurodrive Gmbh & Co. Kg | Gussteil, Planetenträger, Hohlwelle und Planetengetriebe |
JP5033925B1 (ja) | 2011-03-25 | 2012-09-26 | アイシン・エィ・ダブリュ株式会社 | キャリヤ |
DE102011081882A1 (de) | 2011-08-31 | 2013-02-28 | Schaeffler Technologies AG & Co. KG | Getriebevorrichtung mit Stützbolzen für ein Fahrzeug |
CN103797278B (zh) * | 2011-12-16 | 2017-05-03 | 爱信艾达株式会社 | 行星齿轮架 |
US8961359B2 (en) * | 2012-08-07 | 2015-02-24 | Caterpillar Inc. | Planet carrier and clutch housing |
JP6102208B2 (ja) * | 2012-11-19 | 2017-03-29 | アイシン・エィ・ダブリュ株式会社 | 自動変速機 |
JP6119575B2 (ja) * | 2013-11-25 | 2017-04-26 | アイシン・エィ・ダブリュ株式会社 | プラネタリキャリヤ |
JP6162651B2 (ja) * | 2014-06-13 | 2017-07-12 | トヨタ自動車株式会社 | 遊星歯車装置のキャリア |
JP6219783B2 (ja) * | 2014-06-13 | 2017-10-25 | トヨタ自動車株式会社 | 遊星歯車装置のキャリア |
CN105221721A (zh) * | 2015-10-13 | 2016-01-06 | 哈尔滨东安汽车发动机制造有限公司 | 一种行星齿轮架 |
JP6380352B2 (ja) * | 2015-11-26 | 2018-08-29 | トヨタ自動車株式会社 | 車両用自動変速機 |
DE102016125376A1 (de) * | 2016-12-22 | 2018-06-28 | Bühler Motor GmbH | Planetenradträger für ein Umlaufrädergetriebe, Set zur Herstellung eines Umlaufrädergetriebes sowie Umlaufrädergetriebe mit einem solchen Planetenradträger |
DE202018102232U1 (de) * | 2018-04-20 | 2019-07-23 | Hofer Powertrain Gmbh | Mittelstegkonzept bei einem Räderumlaufgetriebe wie einem Planetengetriebe |
DE102018109610A1 (de) | 2018-04-20 | 2019-10-24 | Elringklinger Ag | Planetenträger für ein Räderumlaufgetriebe wie einem Planetengetriebe und entsprechendes Stützverfahren |
US11628942B2 (en) | 2019-03-01 | 2023-04-18 | Pratt & Whitney Canada Corp. | Torque ripple control for an aircraft power train |
EP3931091A4 (en) | 2019-03-01 | 2023-01-11 | Pratt & Whitney Canada Corp. | DISTRIBUTED PROPULSION CONFIGURATIONS FOR AIRCRAFT WITH MIXED PROPULSION SYSTEMS |
US11732639B2 (en) | 2019-03-01 | 2023-08-22 | Pratt & Whitney Canada Corp. | Mechanical disconnects for parallel power lanes in hybrid electric propulsion systems |
EP3941830A4 (en) | 2019-03-18 | 2023-01-11 | Pratt & Whitney Canada Corp. | ARCHITECTURES FOR ELECTRIC HYBRID PROPULSION |
US11486472B2 (en) | 2020-04-16 | 2022-11-01 | United Technologies Advanced Projects Inc. | Gear sytems with variable speed drive |
US11583953B1 (en) * | 2021-08-05 | 2023-02-21 | Schaeffler Technologies AG & Co. KG | Method of forming planetary carrier assembly |
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JP2001304355A (ja) * | 2000-04-25 | 2001-10-31 | Daihatsu Motor Co Ltd | 車両用自動変速機 |
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JP3667775B2 (ja) * | 1991-09-13 | 2005-07-06 | ジヤトコ株式会社 | 自動変速装置 |
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US6434827B1 (en) * | 2000-05-18 | 2002-08-20 | Ford Global Tech., Inc. | Method for creating a gear assembly |
WO2002035116A1 (en) * | 2000-10-23 | 2002-05-02 | Aisin Aw Co., Ltd | Planetary gear set |
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JP2002130392A (ja) | 2000-10-23 | 2002-05-09 | Aisin Aw Co Ltd | プラネタリキャリア |
US7033301B2 (en) * | 2004-02-26 | 2006-04-25 | Ford Global Technologies, Llc | Planet pinion carrier assembly for Ravigneaux gearset |
US6986726B2 (en) * | 2004-02-26 | 2006-01-17 | Ford Global Technologies, Llc | Planet pinion carrier assembly for Ravigneaux gearset |
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2004
- 2004-10-26 JP JP2004310552A patent/JP4715161B2/ja not_active Expired - Fee Related
-
2005
- 2005-09-01 CN CNB200580026007XA patent/CN100451386C/zh not_active Expired - Fee Related
- 2005-09-01 DE DE112005001867T patent/DE112005001867B4/de not_active Expired - Fee Related
- 2005-09-01 WO PCT/JP2005/016462 patent/WO2006046356A1/ja active Application Filing
- 2005-10-25 US US11/257,034 patent/US7316629B2/en not_active Expired - Fee Related
Patent Citations (4)
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JPH0193648A (ja) * | 1987-01-21 | 1989-04-12 | Mazda Motor Corp | 自動変速機の動力伝達装置 |
US5509865A (en) * | 1994-12-14 | 1996-04-23 | General Motors Corporation | Planet gear assembly with a planetary carrier |
JPH10169728A (ja) * | 1996-12-05 | 1998-06-26 | Aisin Aw Co Ltd | ダブルピニオンタイプのプラネタリギヤユニット |
JP2001304355A (ja) * | 2000-04-25 | 2001-10-31 | Daihatsu Motor Co Ltd | 車両用自動変速機 |
Also Published As
Publication number | Publication date |
---|---|
DE112005001867T5 (de) | 2007-09-20 |
JP2006125425A (ja) | 2006-05-18 |
US20060089228A1 (en) | 2006-04-27 |
JP4715161B2 (ja) | 2011-07-06 |
CN1993571A (zh) | 2007-07-04 |
CN100451386C (zh) | 2009-01-14 |
DE112005001867B4 (de) | 2011-03-31 |
US7316629B2 (en) | 2008-01-08 |
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