US20050064981A1 - Shift mechanism for a manual planetary transmission - Google Patents

Shift mechanism for a manual planetary transmission Download PDF

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Publication number
US20050064981A1
US20050064981A1 US10/666,148 US66614803A US2005064981A1 US 20050064981 A1 US20050064981 A1 US 20050064981A1 US 66614803 A US66614803 A US 66614803A US 2005064981 A1 US2005064981 A1 US 2005064981A1
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US
United States
Prior art keywords
control
members
plate
slot
neutral
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
Application number
US10/666,148
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English (en)
Inventor
Raymond Haka
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Motors Liquidation Co
Original Assignee
Motors Liquidation Co
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Motors Liquidation Co filed Critical Motors Liquidation Co
Priority to US10/666,148 priority Critical patent/US20050064981A1/en
Assigned to GENERAL MOTORS CORPORATION reassignment GENERAL MOTORS CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HAKA, RAYMOND J.
Priority to DE102004045160A priority patent/DE102004045160B4/de
Publication of US20050064981A1 publication Critical patent/US20050064981A1/en
Priority to US11/620,066 priority patent/US7707905B2/en
Abandoned legal-status Critical Current

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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
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/28—Final output mechanisms therefor; Actuating means for the final output mechanisms two or more final actuating mechanisms moving the same final output mechanism
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0052—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising six forward speeds
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two sets of orbital 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2097—Transmissions using gears with orbital motion comprising an orbital gear set member permanently connected to the housing, e.g. a sun wheel permanently connected to the housing
    • 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
    • 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
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19219—Interchangeably locked
    • Y10T74/19251—Control mechanism
    • Y10T74/19279—Cam operated
    • 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
    • Y10T74/00—Machine element or mechanism
    • Y10T74/20—Control lever and linkage systems
    • Y10T74/20012—Multiple controlled elements
    • Y10T74/20018—Transmission control
    • Y10T74/20085—Restriction of shift, gear selection, or gear engagement
    • Y10T74/20104—Shift element interlock
    • Y10T74/2011—Shift element interlock with detent, recess, notch, or groove

Definitions

  • This invention relates to transmission controls and, more particularly, to shift mechanisms for a manual planetary transmission.
  • Manual planetary transmissions employ synchronizer type torque-transmitting mechanisms, which are mechanical in nature and are generally controlled by a shift rod, which is under the manipulative control of the operator.
  • synchronizer type torque-transmitting mechanisms which are mechanical in nature and are generally controlled by a shift rod, which is under the manipulative control of the operator.
  • it is necessary to engage and/or disengage two synchronizers to establish a drive ratio through a planetary gear arrangement.
  • One such mechanical shift control mechanism is shown in U.S. Ser. No. 10/443,451, filed May 22, 2003, in the name of Haka and assigned to the assignee of this application.
  • the shift mechanism employs a plurality of plate members having slotted openings formed therein to control one or more shift rails.
  • one of the plate members is a neutral plate, which maintains the shift rods in a neutral position prior to shifting from one ratio to another.
  • each of the plate members has a surface configuration, which will move all of the plates between the shifted plate and the neutral plate upward to release the control rods from the neutral plate.
  • the surface configurations are elongated indentations formed in each plate member.
  • the plates are nested on the surface configurations.
  • each of the plates has a control slot for each of the shift rods necessary to control the synchronizers of a manual planetary transmission.
  • each of the control slots has a neutral slot and a slot perpendicular to the neutral slot.
  • each of the perpendicular slots will provide for continued neutral control or for a shift control for one of the shift control rods.
  • FIG. 1 is a schematic representation of a powertrain describing a manual planetary transmission capable of providing six forward speed ratios and one reverse speed ratio.
  • FIG. 2 is a diagrammatic representation of a portion of the shift control mechanism showing the plates in a neutral position.
  • FIG. 3 is a view similar to FIG. 2 wherein one of the control plates has been moved from the neutral position to an operable position.
  • FIG. 4 is a diagrammatic representation of the slot configuration in the reverse shift control plate for the reverse shift control mechanism.
  • FIG. 5 is a diagrammatic representation of the slot configuration for the 1-2 shift control plate of the shift control mechanism.
  • FIG. 6 is a diagrammatic representation of the slot configuration for the 2-4 shift control plate of the shift control mechanism.
  • FIG. 7 is a diagrammatic representation of the slot configuration for the 5-6 shift control plate of the shift control mechanism.
  • FIG. 8 is a diagrammatic representation of the slot configuration showing the 5-6 shift control plate moved relative to the stacked control plates to the shift ratio position.
  • FIG. 9 is a diagrammatic representation of the slot configuration for the 5-6 control plate wherein the control plate is shifted to the sixth ratio position.
  • FIG. 10 is a diagrammatic representation of an alternative configuration for the shift control mechanism.
  • FIG. 11 is a partial view of the configuration shown in FIG. 10 describing a portion of the shift control mechanism.
  • FIG. 1 a powertrain 10 including a conventional engine 12 , a conventional selectively operable input clutch or torque-transmitting mechanism 14 , and a planetary gear arrangement 16 .
  • the planetary gear arrangement 16 includes two planetary gearsets 18 and 20 , which are combined to form a planetary arrangement.
  • the planetary gearset 18 includes a sun gear member 22 , a ring gear member 24 , and a planet carrier assembly member 26 , which has a plurality of pinion gears 28 rotatably mounted on a planet carrier member 30 and disposed in meshing relationship with both the sun gear member 22 and the ring gear member 24 .
  • the sun gear member 22 is continuously connected to a portion of a transmission housing 32 and is therefore held stationary continuously.
  • the ring gear member 24 is connected with an input shaft 34 , which is also connected with the input clutch or torque-transmitting mechanism 14 .
  • the planet carrier member 30 is drivingly connected with a mechanical torque-transmitting mechanism or synchronizer 36 and also with a mechanical torque-transmitting mechanism or synchronizer 38 .
  • the input shaft 34 is drivingly connected with a mechanical torque-transmitting mechanism or synchronizer 40 .
  • Each of the mechanical torque-transmitting mechanisms 36 , 38 , and 40 are conventional synchronizer type shift mechanisms, which are well known in the art.
  • the torque-transmitting mechanisms 36 and 40 are rotating type torque-transmitting mechanisms, which are generally referred to as clutches.
  • the torque-transmitting mechanism 38 is a dual purpose synchronizer and provides a rotating type torque-transmitting mechanism when connected with the planet carrier member 30 and a stationary type torque-transmitting mechanism or brake when connected with the transmission housing 32 .
  • the planetary gearset 20 is a gearset commonly referred as a Ravigneaux type gearset.
  • This gearset 20 includes two sun gear members 42 and 44 , a ring gear member 46 , and a planet carrier assembly member 48 .
  • the planet carrier assembly member 48 includes a plurality of long pinion gears 50 and a plurality of short pinion gears 52 .
  • the long pinion gears 50 mesh continuously with the sun gear member 42 and the ring gear member 46 .
  • the short pinion gears 52 mesh continuously between the sun gear member 44 and the long pinion gears 50 .
  • the planetary connection between the sun gear member 42 and the ring gear member 46 is a simple planetary gear connection while the connection between the sun gear member 44 and the ring gear member 46 is a compound connection.
  • the ring gear member 46 is continuously drivingly connected with a transmission output shaft 54 , which in turn is connected to drive the vehicle wheels in a well known manner.
  • the pinion gears 50 and 52 are rotatably mounted on a planet carrier member 56 , which is drivingly connected with a portion of the mechanical torque-transmitting mechanism 40 and also drivingly connected with a portion of a mechanical torque-transmitting mechanism or synchronizer 58 .
  • the mechanical torque-transmitting mechanism 58 is a synchronizer type torque transmitter, which is effective to selectively connect the planet carrier member 56 to the transmission housing 32 and therefore operates as a brake.
  • synchronizers have a neutral condition and at least one active condition.
  • the torque-transmitting mechanisms 36 , 40 , and 58 all have a neutral condition and an active condition.
  • the active condition of torque-transmitting mechanism 36 the planet carrier member 30 is drivingly connected with the sun gear member 44 .
  • the input shaft 34 is drivingly connected with the planet carrier member 56 .
  • the active condition of the torque-transmitting mechanism 58 the planet carrier member 56 is connected with the stationary housing 32 . Obviously, the torque-transmitting mechanisms 40 and 58 would not be engaged at the same time.
  • the torque-transmitting mechanism 38 is a three-position synchronizer having two active positions and a neutral position. In one active position, the synchronizer 38 provides a drive connection between the planet carrier member 30 and the sun gear member 42 . In another active position, the synchronizer or torque-transmitting mechanism 38 provides a braking connection between the sun gear member 42 and the transmission housing 32 .
  • the synchronizer 36 has two positions A and B, A being the neutral position and B being the drive connection position.
  • the synchronizer 38 has three positions A, B, and C, C being the neutral position, A being the braking position, and B being the rotating drive connection.
  • the synchronizer 40 has two positions A and B, A being the neutral position and B being a drive position connecting the input shaft 34 to the planet carrier member 56 .
  • the synchronizer 58 has two conditions A and B, B being the neutral condition and A being the braking condition in which the planet carrier member 56 is connected with the transmission housing 32 .
  • the synchronizers 36 , 40 , and 58 are always shifted from neutral in one direction of operation while the synchronizer 38 is shifted from neutral to an operating condition either side of neutral.
  • FIG. 2 Shown diagrammatically in FIG. 2 is a portion of a shift control mechanism incorporating four control shift plates 60 , 62 , 64 , and 66 , and a neutral plate 68 .
  • the neutral plate 68 is held stationary in the lateral directions and is permitted to move vertically along a pair of pins or pegs 70 and 72 .
  • the plate 68 is urged downwardly by springs 74 and 76 .
  • the plate 60 is the reverse plate
  • plate 62 is the 1-2 shift control plate
  • the plate 64 is the 3-4 shift control plate
  • the plate 66 is the 5-6 shift control plate.
  • a shift control rod 78 which is typical of the four shift control rods necessary to operate the four synchronizers 36 , 38 , 40 , and 58 .
  • the shift control rod 78 is movable in the direction of Arrow D and includes a vertical or upright pin portion 80 , which is engaged with each of the plates 60 , 62 , 64 , 66 , and 68 .
  • the engagement with the plate 68 is by way of a circular opening 82 .
  • Another circular opening 84 can also be seen, which is the opening for the engagement of a pin member 86 of another control rod, not shown.
  • the shift control plate 66 which is the 5-6 control plate, has been moved from the neutral position shown in FIG. 2 to the fifth ratio position.
  • Each of the plates 60 , 62 , 64 , 66 , and 68 has a pair of longitudinally extending indentations or surface characteristics 87 and 88 .
  • these indentations 87 and 88 are aligned or nested such that the plates are stacked substantially in contact.
  • plate 66 is moved laterally, the indentations 87 and 88 move laterally with that plate while the remaining indentations are moved vertically relative to the plate 66 .
  • the plates 60 , 62 , 64 , and 68 are moved a distance of twice the height of the indentations 87 and 88 .
  • the indentations 87 and 88 move out of respective stationary control indentations 90 and 92 and therefore lift all of the plates one height of the indentation.
  • the indentations 87 and 88 of the plate 64 abut a flat surface on the plate 66 which is therefore also move vertically the height of the indentations 87 and 88 .
  • the stack of plates above the plate 66 are moved vertically a distance equal to the height of twice of the indentations.
  • the control rod 78 is effective to control the operation of the synchronizer 36 and is therefore moved with the 1-2 shift plate 60 and the 3-4 shift plate 64 .
  • FIG. 4 is a representation of the reverse plate 60 .
  • the reverse plate 60 as does each of the control plates, has four control slots 94 , 96 , 98 , and 100 .
  • the control slot 94 has a neutral slot portion 102
  • the control slot 96 has a neutral slot portion 104
  • the control slot 98 has a neutral slot portion 106
  • the slot 100 has a neutral slot portion 108 .
  • Each of the control slots 94 , 96 , 98 , and 100 also have respective shift control slots 110 , 112 , 114 , and 116 .
  • the control pin 80 is located in the slot 96 , which is the control slot for the synchronizer 36 .
  • the control slot 94 houses the control pin 86
  • the control slot 98 houses a control pin 118
  • the control pin 100 houses a control pin 120 .
  • the control pin 86 is effective to control the synchronizer 40 .
  • the control pin 118 is effective to control the synchronizer 38 .
  • the control pin 120 is effective to control the synchronizer 58 . If the plate 60 is moved in the direction of Arrow R, the pins 86 and 80 will remain in the slot 110 and in the neutral slots 102 and 104 . However, the pins 118 and 120 will be moved to the right in the slots 114 and 116 .
  • the synchronizer 58 will ground the carrier 56 at position 58 B ( FIG. 1 ) and the synchronizer 38 will connect the carrier 30 with the sun gear member 42 . This will establish a reverse drive between the sun gear member 42 and the ring gear member 46 and therefore with the output shaft 54 .
  • the slots 94 A, 96 A, 98 A, and 100 A of the shift control plate 62 are shown.
  • the slot 94 A aligns in the neutral position with the slot 94
  • the slot 96 A aligns in the neutral position with the slot 96
  • the slot 98 A aligns in the neutral position with the slot 98
  • the slot 100 A aligns in the neutral position with the slot 100 .
  • the plate 62 is manipulated whenever a neutral-to-first or a neutral-to-second shift is desired. For a shift to first gear, the plate 62 is shifted downward, as seen in FIG. 5 , and for the second ratio, the plate 62 is shifted upward, as seen in FIG. 5 , in the direction of Arrow E.
  • the shifting of the plate 62 will enforce the plates 60 and 68 to move upward thereby releasing the pins 80 , 86 , 118 , and 120 .
  • the manipulation of the plate 62 downward in the direction of Arrow E will cause the pin 80 to move rightward in the slot 96 A and also cause the pin 120 to move rightward in the slot 100 A.
  • This will cause manipulation of the synchronizers 36 and 58 while retaining the synchronizers 38 and 40 in the neutral position as controlled by the slots 94 A and 98 A as well as the neutral slot 102 and 106 .
  • the slot configuration of the 3-4 shift control plate 64 is shown in FIG. 6 .
  • the 3-4 shift control plate 64 has formed therein slots 94 B, 96 B, 98 B, and 100 B, which are aligned in a neutral position with the slots 94 , 94 A, 96 , 96 A, 98 , 98 A, and 100 , 10 A.
  • the 3-4 shift control plate 64 is manipulated by the control mechanism when the operator desires to establish either the third forward speed ratio or the fourth forward speed ratio.
  • the plate 64 is moved downward in the direction of Arrow F such that the pin 80 will move rightward in the slot 96 B, the pin 118 will move rightward in the slot 98 B, and the pins 120 and 86 will remain in the neutral position.
  • the pins 80 and 118 move rightward, they are also retained along the neutral plane in the respective neutral slots 104 and 106 of the plates 60 , 62 , and 66 .
  • the fourth forward speed ratio will be established.
  • the pin 86 will be moved rightward along the slot 94 B
  • the pin 80 will be moved rightward along the slot 96 B
  • the pins 118 and 120 will remain in the neutral position as controlled by the slots 98 B, 100 B, 106 and 108 .
  • the synchronizer 40 will be manipulated to engage the input shaft 34 with the planet carrier member 56 and will manipulate the synchronizer 36 to engage the planet carrier member 30 with the sun gear member 44 . This will provide two forward input rotations to the Ravigneaux planetary gearset 20 , which will result in a forward rotation of the output shaft 54 .
  • the slot configuration of the 5-6 shift control plate 66 is shown in FIG. 7 .
  • the plate 66 is moved downward in the direction of Arrow G to the fifth position and upward in the direction of Arrow G from the neutral position to the sixth position.
  • the plate 66 has been moved upward relative to the stack of plates in the direction of arrow G such that the pin 86 is moved rightward by the interaction of the slots 94 C and 102 , the pin 120 is moved leftward by the interaction of the slots 100 C and 108 , while the pins 80 and 118 remain in the neutral position by the interaction of their respective slots 96 C, 104 and 98 C, 106 .
  • the manipulation of the plate 66 upward in the direction of Arrow G will result in the pin 118 being returned to the neutral position while the pin 120 is moved leftward.
  • the pin 120 manipulates the synchronizer 58 to provide a ground connection at the sun gear member 42 while the synchronizer 38 is returned to the neutral thereby disconnecting the planet carrier member 30 from the sun gear member 42 .
  • the Ravigneaux gearset 20 is placed in a high overdrive condition thereby resulting in a forward rotation of the output shaft 54 .
  • FIG. 10 An alternative embodiment of a shift control mechanism 200 is shown in FIG. 10 .
  • a plurality of tubular members 202 , 204 , 206 , and 208 are nested and they surround the transmission, which is not shown.
  • Each of the tubular members 202 , 204 , 206 , and 208 have respective control connectors 210 , 212 , 214 , and 216 .
  • the control connectors each have respective slot portions 220 , 222 , 224 , and 226 .
  • a conventional shift control mechanism having a rod end is manipulable among the slots 220 , 222 , 224 , and 226 to establish which of the tubular members 202 , 204 , 206 , and 208 will be manipulated by the control mechanism.
  • Each of the tubular members 202 , 204 , 206 , and 208 have slots formed therein, one set of the slots is shown in FIG. 10 .
  • the slot configurations are substantially identical with the slot configurations shown above in FIGS. 4 through 7 .
  • the rotation of the tubular members 202 , 204 , 206 , and 208 results in similar movement of control pins 80 , 86 , 118 , and 120 , and thereby manipulation of the synchronizers 36 , 38 , 40 , and 58 .
  • a conventional manual control mechanism i.e. rod and linkage or flexible push-pull cable
  • a conventional hydraulically actuated system or a conventional electrically actuated system, or a conventional electro-hydraulically actuated system can be employed.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)
  • Gear-Shifting Mechanisms (AREA)
US10/666,148 2003-09-18 2003-09-18 Shift mechanism for a manual planetary transmission Abandoned US20050064981A1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US10/666,148 US20050064981A1 (en) 2003-09-18 2003-09-18 Shift mechanism for a manual planetary transmission
DE102004045160A DE102004045160B4 (de) 2003-09-18 2004-09-17 Steuermechanismus für ein handgeschaltetes Planetengetriebe
US11/620,066 US7707905B2 (en) 2003-09-18 2007-01-05 Shift mechanism for a manual planetary transmission

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US10/666,148 US20050064981A1 (en) 2003-09-18 2003-09-18 Shift mechanism for a manual planetary transmission

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US11/620,066 Continuation-In-Part US7707905B2 (en) 2003-09-18 2007-01-05 Shift mechanism for a manual planetary transmission

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US20050064981A1 true US20050064981A1 (en) 2005-03-24

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US10/666,148 Abandoned US20050064981A1 (en) 2003-09-18 2003-09-18 Shift mechanism for a manual planetary transmission
US11/620,066 Expired - Fee Related US7707905B2 (en) 2003-09-18 2007-01-05 Shift mechanism for a manual planetary transmission

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US11/620,066 Expired - Fee Related US7707905B2 (en) 2003-09-18 2007-01-05 Shift mechanism for a manual planetary transmission

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DE (1) DE102004045160B4 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10378616B2 (en) * 2016-10-26 2019-08-13 Zf Friedrichshafen Ag Transmission for a vehicle

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011124975A1 (en) * 2010-04-06 2011-10-13 Kongsberg Automotive Ab Shift fork assembly
CN102913598B (zh) * 2012-10-30 2016-03-23 顺德职业技术学院 行星齿轮式手动变速器
US9222574B2 (en) 2013-03-20 2015-12-29 Gm Global Technology Operations, Llc Cantilever spring type detent assembly
US9347549B2 (en) 2013-03-20 2016-05-24 Gm Global Technology Operations, Llc Gear engagement mechanism
DE102016202723B4 (de) * 2016-02-23 2018-01-11 Schaeffler Technologies AG & Co. KG Hochübersetzendes Umlaufräderschaltgetriebe, insbesondere für ein elektrisch betriebenes Kraftfahrzeug

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1944331A (en) * 1932-07-30 1934-01-23 Gen Motors Corp Synchronized transmission mechanism
US5740695A (en) * 1996-01-29 1998-04-21 Ford Global Technologies, Inc. Shift device for a manual transmission
US6026698A (en) * 1996-08-13 2000-02-22 Weston; Bevan Transmission and shift mechanism
US20040142787A1 (en) * 2001-01-23 2004-07-22 Rodney Milbourne First stage clutch
US6835157B2 (en) * 2003-05-22 2004-12-28 General Motors Corporation Apparatus for controlling a plurality of synchronizers in a manual planetary transmission

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1122468B1 (de) * 2000-02-04 2003-05-07 Ford Global Technologies, Inc., A subsidiary of Ford Motor Company Schaltvorrichtung für ein Wechselgetriebe eines Kraftfahrzeuges

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1944331A (en) * 1932-07-30 1934-01-23 Gen Motors Corp Synchronized transmission mechanism
US5740695A (en) * 1996-01-29 1998-04-21 Ford Global Technologies, Inc. Shift device for a manual transmission
US6026698A (en) * 1996-08-13 2000-02-22 Weston; Bevan Transmission and shift mechanism
US20040142787A1 (en) * 2001-01-23 2004-07-22 Rodney Milbourne First stage clutch
US6835157B2 (en) * 2003-05-22 2004-12-28 General Motors Corporation Apparatus for controlling a plurality of synchronizers in a manual planetary transmission

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10378616B2 (en) * 2016-10-26 2019-08-13 Zf Friedrichshafen Ag Transmission for a vehicle

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US7707905B2 (en) 2010-05-04
DE102004045160B4 (de) 2008-10-16
DE102004045160A1 (de) 2005-05-12
US20070107543A1 (en) 2007-05-17

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