WO2014084282A1 - Dispositif de changement de vitesse - Google Patents

Dispositif de changement de vitesse Download PDF

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Publication number
WO2014084282A1
WO2014084282A1 PCT/JP2013/081972 JP2013081972W WO2014084282A1 WO 2014084282 A1 WO2014084282 A1 WO 2014084282A1 JP 2013081972 W JP2013081972 W JP 2013081972W WO 2014084282 A1 WO2014084282 A1 WO 2014084282A1
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WO
WIPO (PCT)
Prior art keywords
shift
reverse
gear
meshing
spring
Prior art date
Application number
PCT/JP2013/081972
Other languages
English (en)
Japanese (ja)
Inventor
隆浩 中里
竜司 成田
敬治 竹下
櫻井　敦
Original Assignee
アイシン・エーアイ株式会社
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 アイシン・エーアイ株式会社 filed Critical アイシン・エーアイ株式会社
Publication of WO2014084282A1 publication Critical patent/WO2014084282A1/fr

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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
    • 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
    • F16H63/30—Constructional features of the final output mechanisms
    • F16H63/302—Final output mechanisms for reversing
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
    • B60Y2400/00—Special features of vehicle units
    • B60Y2400/40—Actuators for moving a controlled member
    • B60Y2400/418—Power assistance, e.g. servo-motors
    • B60Y2400/4185—Mechanical assistance, i.e. using springs or accumulators without feedback control
    • 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
    • F16H63/30—Constructional features of the final output mechanisms
    • F16H2063/3089—Spring assisted shift, e.g. springs for accumulating energy of shift movement and release it when clutch teeth are aligned

Definitions

  • the present invention relates to a shift device, and more particularly to a shift device configured to apply a load by a spring when moving a reverse idler gear to a meshing position with a power transmission gear.
  • Patent Document 1 there are provided a shift arm which is provided in a casing and swings by being reverse shifted by a driver, a reverse idler gear which slides in an axial direction by swinging the shift arm, and A shift device is disclosed that includes biasing means provided on the casing side and a cam portion formed on the shift arm side of the biasing means.
  • the cam portion includes a spring and a ball member as biasing means, a first step portion, a second step portion and a third step portion along the moving direction of the shift arm at a position facing the ball member, and these steps
  • An inclined step is formed, which comprises a first inclined surface and a second inclined surface located between the parts.
  • the ball member biasing the first step portion by the pressing force (load) of the spring is moved to the first inclined surface and the second inclined surface. It is moved until it abuts on the third step while pressing in order of the inclined surface. Thereby, the reverse idler gear meshes with the power transmission gear at the meshing position.
  • the first step, the second step, the third step, the first inclined surface, and the second slope are provided on the cam portion to apply the operation force of the shift arm.
  • the structure of the shift device is complicated because the surface is formed and a spring and a ball member are required to press the first inclined surface and the second inclined surface.
  • the present invention is made in view of the above-mentioned subject, and it aims at providing a shift device which can generate load which shifts a gear certainly by simple structure.
  • the shift device according to the present invention is configured as follows.
  • the shift device comprises: a shift fork that slides by performing a reverse shift operation, a shift arm that swings via the shift fork, and an axial direction of a reverse idler gear by swinging the shift arm It is premised that a spring is provided to apply a load to the shift arm so as to slide in the sliding direction of the idler gear, and the reverse idler gear is engaged with the power transmission gear to constitute a reverse gear.
  • the load applying direction of the spring is the reverse idler gear and the power transmission. It is characterized in that it is switched in the direction of meshing with the gear.
  • the shift device having such a configuration, by switching the load application direction of the spring to the direction in which the reverse idler gear and the power transmission gear are engaged, it is possible to generate a load for shifting the gear reliably with a simple structure. .
  • the meshing position of the reverse idler gear and the power transmission gear it is possible to suppress that the reverse idler gear is stopped before the slide (stroke) is completed.
  • torque input is performed in a state in which the meshing length of the gear is sufficient, breakage of the reverse idler gear can be suppressed.
  • the elastic force of the spring is set larger than the frictional force at the meshing position of the reverse idler gear and the power transmission gear.
  • the elastic force of the spring is made larger than the frictional force (sliding resistance) of the reverse idler gear prior to the meshing position of the reverse idler gear and the power transmission gear. It is possible to prevent the slide (stroke) from stopping in an incomplete state.
  • the shift fork and the shift arm mesh with the reverse idler gear and the power transmission gear in meshing direction or Between the shift fork and the shift arm, there is provided a clearance region in which the shift fork and the shift arm do not contact with each other between the shift fork and the shift arm. It is characterized by According to this structure, while the shift fork is passing through the clearance area, the shift arm can be quickly rocked in the meshing direction by the pressing load in the meshing direction of the spring. The force (sliding resistance) can easily pass through the area where the elastic force of the spring is larger. As a result, it is possible to prevent the reverse idler gear from stopping in an incomplete meshing state.
  • the shift arm is formed with an engagement hole through which the shift fork is inserted, and the clearance area includes an engagement hole of the shift arm and the shift fork. And at least in a direction along the axial direction. According to this structure, an axial clearance can be easily formed between the shift arm and the shift fork.
  • the engagement hole of the shift arm is formed in an elliptical shape in which a length in a direction orthogonal to the axial direction is larger than a length in the axial direction.
  • the shift device of the present invention it is possible to generate a load capable of reliably shifting gears with a simple structure.
  • FIG. 2 is a cross-sectional view taken along line 100-100 of FIG. 1; It is a top view which shows the neutral state of a shift fork and a shift arm. It is a top view which shows the reverse state of a shift fork and a shift arm. It is a graph (analysis result) which shows the relationship between stroke on a fork shaft, and a spring load. It is a graph (analysis result) which shows the relation between the knob top stroke and the knob top load. It is a graph (experimental result) which shows the relationship between a knob top stroke and a knob top load.
  • a countershaft (speed-change shaft) 12 connected to the engine side via an input shaft 11 and a reduction gear pair, and an output connected to the drive wheel side
  • a shaft (speed-change shaft) 13 is rotatably supported in parallel with each other in the vertical direction.
  • a plurality of pairs of transmission gears are provided between the countershaft 12 and the output shaft 13, a plurality of pairs of transmission gears (only two pairs of transmission gears are shown by reference numerals 20Aa, 20Ab, and 20Ba, 20Bb) are provided.
  • the transmission gears 20Ab and 20Bb provided on the countershaft 12 and the transmission gears 20Aa and 20Ba provided on the output shaft 13 are engaged with each other in corresponding pairs.
  • Gear pieces 21 and 22 are coaxially press-fitted and fixed on opposite sides of both transmission gears 20Aa and 20Ba.
  • a clutch hub 15 is fixed to an output shaft 13 located between the two transmission gears 20Aa and 20Ba.
  • a sleeve 16 is slidably spline-engaged on the outer periphery of the clutch hub 15.
  • the inner peripheral splines of the sleeve 16 are also selectively engageable with the outer peripheral splines of the gear pieces 21 and 22 located on one side of the clutch hub 15.
  • synchromesh mechanism consisting of a conical surface formed on the synchronizer rings 23 and 24 and the gear pieces 21 and 22 respectively.
  • the same synchromesh mechanism as described above is also provided for the transmission gears without the reference numerals, but the detailed description will be omitted.
  • the casing 10 is provided with a fork shaft 25 and a guide shaft 25 a so as to be movable and fixed parallel to the counter shaft 12 and the output shaft 13 respectively.
  • a shift fork 26 supported by each of the shafts 25 and 25a is engaged with an annular groove 16a (see FIG. 1) formed at its tip end on the outer periphery of the sleeve 16.
  • the sleeve 16 In the inoperative state, the sleeve 16 is held at the neutral position shown in FIG. 1 and is disengaged from any of the splines on the outer periphery of both gear pieces 21 and 22.
  • the shift fork 26 As the shift fork 26 is axially reciprocated and slid by the fork shaft 25 (see FIG. 2), the shift fork 26 is selectively engaged with one of the splines on the outer periphery of both gear pieces 21 and 22.
  • the sleeve is slid by the shift fork and engaged with the spline of the gear piece in the same manner as described above. A detailed description of this point is omitted.
  • the transmission gears are switched such that power is transmitted between the countershaft 12 and the output shaft 13 by a pair of transmission gears meshing with each other.
  • the reverse output gear 17 is integrally formed on the outermost periphery of one of the plurality of sleeves 16 that are normally provided.
  • the reverse input gear 18 is fixed to the counter shaft 12.
  • the reverse input gear 18 is disposed at a position substantially corresponding in the axial direction to the clutch hub 15 provided with the sleeve 16.
  • the reverse output gear 17 and the reverse input gear 18 are examples of the “power transmission gear” in the present invention.
  • a reverse shaft 14 is fixedly supported by the casing 10 in parallel with the counter shaft 12 and the output shaft 13 and on the side of the counter shaft 12.
  • a reverse idler gear 19 is rotatably and axially slidable on the reverse shaft 14.
  • the reverse idler gear 19 is in an open position (opening direction) (neutral state) separated from any of the reverse input gear 18 of the counter shaft 12 and the reverse output gear 17 of the output shaft 13, the reverse output gear 17 and the reverse input gear 18. It is slidable between a meshing position (meshing direction) (a reverse state shown by a two-dot chain line in FIG. 1) meshing with both.
  • the chamfered portion when the reverse idler gear 19 is in the meshing position, the chamfered portion also has a similar inclined surface at the tip of each tooth 17a of the reverse output gear 17 which starts meshing with the tooth 19a of the reverse idler gear 19. 17a1 is formed.
  • the reverse idler gear 19 is integrally formed with a cylindrical portion 19b slidably fitted on the outer periphery of the reverse shaft 14 on the opposite side of the tooth portion 19a from the chamfered portion 19a1.
  • An annular groove 19c is formed in the cylindrical portion 19b.
  • the tooth portions 17a, 18a and 19a are examples of the "gear meshing portion" in the present invention.
  • the shift device 2 is disposed in the casing 10.
  • the shift device 2 mainly includes a shift arm 30, a control shaft 31, a shift fork 32, a pin 33, a bracket 34, a spring 35, and the like.
  • the shift arm 30 slides the reverse idler gear 19 between the open position (neutral state) and the meshing position (reverse position).
  • the shift arm 30 extends upward from the end 30 a of the counter shaft 12 opposite to the side on which the reverse shaft 14 is provided, through the lower side of the counter shaft 12.
  • the tip 30 b of the shift arm 30 is engaged in an annular groove 19 c (see FIG. 1) of the reverse idler gear 19.
  • a boss 30c is formed at a position separated from the end 30a.
  • an engagement hole 30d extending in a direction orthogonal to the counter shaft 12 is formed.
  • the length in the extending direction of the shift arm 30 of the engagement hole 30d has an elliptical shape larger than the length in the direction orthogonal to the extending direction of the shift arm 30 in plan view, as shown in FIGS. doing.
  • the length in the axial direction (the sliding direction of the reverse idler gear 19) of the reverse shaft 14 of the engagement hole 30d is smaller than the length in the direction orthogonal to the axial direction.
  • control shaft 31 is provided movable and fixed in parallel to the counter shaft 12 and the output shaft 13.
  • a drive pin 32a formed at the tip of a downwardly extending arm portion is coaxially inserted into the engagement hole 30d of the shift arm 30 via the shift fork 32 to support the shift arm 30.
  • the control shaft 31 is driven in response to the driver's operation of a shift knob (reverse shift) (not shown) provided inside the vehicle (indoor).
  • the end 30 a of the shift arm 30 is rotatably and slidably supported by the pin 33 via the bracket 34 on the casing 10.
  • the pin 33 is provided in parallel with the drive pin 32a.
  • the bracket 34 is attached in the casing 10 by a screw member 34 a or the like.
  • the spring 35 has one end 35 a on the counter shaft 12 side and the other end 35 b on the opposite side to the counter shaft 12.
  • One end 35 a is attached to the engagement hole 30 e of the shift arm 30.
  • the other end 35 b is attached to the engaging portion 34 b of the bracket 34.
  • the spring 35 applies a pressing force (load) to the bracket 34 on the neutral side and the reverse side of the shift arm 30.
  • a predetermined clearance area A is provided between the drive pin 32 a of the shift fork 32 and the engagement hole 30 d of the shift arm 30.
  • the clearance area A is provided on the neutral side of the drive pin 32a of the shift fork 32 when the reverse idler gear 19 is in the open position (neutral state), as shown in FIG.
  • the contact portion 30 f formed on the neutral side of the engagement hole 30 d of the shift arm 30 is in a state of being in contact with the bracket 34.
  • the clearance area A is provided on the reverse side of the drive pin 32 a of the shift fork 32.
  • the load of the spring 35 acts on the reverse side of the shift arm 30.
  • the neutral side portion of the drive pin 32 a of the shift fork 32 is in a state of being fixed to the reverse side in contact with the neutral side portion of the engagement hole 30 d of the shift arm 30. That is, when the shift arm 30 moves from the open position (neutral state) to the meshing position (reverse position) (in the middle of movement), the load direction of the spring 35 is switched.
  • the control shaft 31 (see FIG. 2) and the shift fork 32 are axially reciprocated in response to the driver's operation of the shift knob provided in the vehicle.
  • the tip end portion 30 b of the shift arm 30 slides and reciprocates around the pin 33.
  • the reverse idler gear 19 is reciprocated and slid between a separated position (neutral state) separated from both the reverse input gear 18 and the reverse output gear 17 and a meshing position (reverse state) meshing with each gear.
  • Ru
  • the spring 35 provided between the shift arm 30 and the bracket 34 is a load on the way the reverse idler gear 19 moves from the open position (neutral state) to the meshing position (reverse state).
  • the direction is configured to switch from the neutral side to the reverse side.
  • the load arm of the spring 35 acts on the neutral side. It is in a state of being pressed to the neutral side. In this state, the drive pin 32a of the shift fork 32 and the engagement hole 30d of the shift arm 30 are in contact at the reverse side, and the clearance area A is provided at the neutral side. .
  • the shift fork 32 moves to the reverse side to move the shift arm 30 to the reverse side (a load (biasing force) of the spring 35). Swing to). Then, when the shift arm 30 swings a predetermined distance, the shift arm 30 gradually separates from the drive pin 32 a of the shift fork 32 in the reverse direction. That is, the shift arm 30 swings in the direction (reverse side) in which the clearance area A with the shift fork 32 (drive pin 32a) is closed. At this time, the drive pin 32 a of the shift fork 32 and the engagement hole 30 d of the shift arm 30 do not come in contact with each other.
  • the horizontal axis in FIG. 5 indicates the on-shaft stroke [mm].
  • the on-shaft stroke [mm] is a stroke (movement amount) of the control shaft 31 and the shift fork 32.
  • the vertical axis in FIG. 5 indicates the spring load [N].
  • the spring load [N] is a load that the spring 35 applies to the shift arm 30.
  • the spring load shown on the vertical axis indicates that the load is applied to the neutral side at the upper side with respect to 0 [N], and the load at the reverse side with respect to 0 [N]. It shows that it is given.
  • the spring on the neutral side of the spring 35 is within the range of 0 [mm] or more and less than about 5.5 [mm] on the shaft. Load decreases gently (decreases).
  • a point at which the load direction of the spring 35 switches from the neutral side to the reverse side is a load direction switching point.
  • the load direction switching point substantially coincides with a meshing start point (meshing position) at which meshing with both of the reverse idler gear 19 and the reverse input gear 18 (reverse output gear 17) starts. Further, the load (pressure force) of the spring 35 at the meshing start point is set to be larger than the sliding resistance (frictional resistance) of the reverse idler gear 19 to the reverse shaft 14.
  • the load direction switching point may be a slide position (a range in which the stroke on the shaft is smaller than 5.5 [mm]) before the meshing start point (meshing position) is reached.
  • the shift arm 30 automatically moves to the reverse side (is self-propelled) by the load on the reverse side of the spring 35. That is, a suction load on the reverse side is generated such that the shift knob (shift arm 30) automatically moves without the driver applying a force to the shift knob.
  • the spring 35 reverses by a pressing force having a size that resists the sliding resistance between the reverse idler gear 19 and the reverse shaft 14. It is necessary to push it to the side (make it run).
  • the sliding resistance area is shown in a predetermined area B with respect to the load 0 [N] of the spring 35.
  • the load (pressure) of the spring 35 is smaller than the sliding resistance shown in the region B, the reverse idler gear 19 may stop halfway without shifting to the reverse side.
  • the increase and decrease of the spring load is gradual, and the reverse idler gear 19 It may stop halfway without shifting to the reverse side.
  • the reverse idler gear 19 since the magnitude of the spring load changes rapidly at the load direction switching point, the reverse idler gear 19 does not shift to the reverse side and does not stop halfway. It becomes possible to make the stroke of the stroke 19 complete until the shift on the reverse side is completed.
  • FIG. 6A on the horizontal axis, the knob on-stroke [mm] of the shift knob operated by the driver and the meshing length [mm] between the reverse idler gear 19 and the reverse input gear 18 (or reverse output gear 17)
  • the vertical axis shows the on-knob load [N] which is the force applied by the driver to the shift knob.
  • FIG. 6B shows the meshing lengths (0 [mm]) of the reverse idler gear 19 and the reverse input gear 18 (or reverse output gear 17).
  • FIG. 6C shows the meshing lengths (12.3 [mm]) of the reverse idler gear 19 and the reverse input gear 18 (or the reverse output gear 17).
  • FIG. 6D shows the meshing lengths (17.5 [mm]) of the reverse idler gear 19 and the reverse input gear 18 (or reverse output gear 17).
  • the knob load is maximum when the knob stroke is in the range of 10 mm to 20 mm, and then the knob stroke is 52.8 mm. It decreases gradually until it becomes.
  • the spring 35 applies a load that presses the shift arm 30 to the reverse side, and the knob top load is gentle. Decrease.
  • the stroke on the knob is about 52.8 [mm] or more and about 77.5 [mm] or less (area E: shaded area)
  • area E shaded area
  • the load on the reverse side of the spring 35 allows the driver to operate the shift knob with no or relatively small force on the shift knob.
  • the conventional example shown by the broken line in FIG. 6 since the on-knob load is always applied regardless of the on-knob stroke size, it can be understood that the driver always applies force to the shift knob .
  • the meshing length between the reverse idler gear 19 and the reverse input gear 18 (or the reverse output gear 17) is approximately It becomes 0 [mm].
  • the meshing length between the reverse idler gear 19 and the reverse input gear 18 (or the reverse output gear 17) is It will be about 12.3 [mm].
  • the safety factor is about 1.
  • the load on the reverse side of the spring 35 is maximum in the range where the knob top stroke is about 70.0 [mm] or more and about 80.0 [mm] or less.
  • the horizontal axis indicates the on-knob stroke [mm] of the shift knob operated by the driver
  • the vertical axis indicates the knob, which is the magnitude of the force applied by the driver to the shift knob.
  • the upper load [N] is shown.
  • the on-knob load is maximized when the on-knob stroke is about 15 [mm] and then gradually decreases until the on-knob stroke reaches the meshing start point. And, when the knob-on-stroke is the meshing start point, the knob-on load is rapidly decreasing.
  • the load on the shift knob is also switched from the neutral side to the reverse side by switching the load direction of the spring 35 attached to the shift arm 30 from the neutral side to the reverse side. Become. This allows the driver to operate the shift knob with no or relatively small force on the shift knob. Such an effect is verified also in an actual vehicle.
  • the elastic force of the spring 35 is set to the friction force at the meshing start point of the teeth 17a to 19a of the reverse idler gear 19 and the reverse input gear 18 (reverse output gear 17). Dynamic resistance). Thereby, the elastic force of the spring 35 is made larger than the frictional force (sliding resistance) of the reverse idler gear 19 before the meshing start point of the reverse idler gear 19 and the reverse input gear 18 (reverse output gear 17). Thus, it is possible to prevent the slide (stroke) of the reverse idler gear 19 from being stopped in an incomplete state.
  • the shift fork 32 and the shift arm 30 are brought into contact in the meshing direction (reverse side) in the region where the elastic force of the spring 35 is larger than the frictional force at the meshing start point.
  • a clearance region A where the shift fork 32 and the shift arm 30 do not contact is provided.
  • the shift arm 30 can be quickly swung to the reverse side by the pressing load on the reverse side of the spring 35.
  • a region where the frictional force (sliding resistance) is larger than the elastic force of the spring 35 can be easily passed. As a result, it is possible to prevent the reverse idler gear 19 from stopping in an incomplete meshing state.
  • the clearance area A is provided in at least the direction along the axial direction between the engagement hole 30 d of the shift arm 30 and the shift fork 32.
  • the clearance area A along the axial direction can be easily formed between the shift arm 30 and the shift fork 32.
  • the engagement hole 30 d of the shift arm 30 is formed into an elliptical shape whose length in the direction orthogonal to the axial direction is larger than the axial direction length of the reverse shaft 14. .
  • this invention is not limited to this.
  • any shape other than the elliptical shape may be used.
  • the present invention is applicable to a shift device, and more specifically, to a shift device configured to apply a pressing force by a spring when moving a reverse idler gear to a meshing position.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gear-Shifting Mechanisms (AREA)

Abstract

L'invention concerne un dispositif de changement de vitesse permettant de générer une charge en vue d'obtenir un changement de vitesse fiable grâce à une configuration simple. Pour le dispositif de changement de vitesse (2), dans une position coulissante avant le point auquel les dents (17a - 19a) d'un pignon intermédiaire de marche arrière (19) et d'un pignon d'entrée en marche arrière (18) (pignon de sortie de marche arrière (17)) commencent à s'engrener, la direction d'application de charge d'un ressort (35) commute vers une direction (coté arrière) qui amène le pignon intermédiaire de marche arrière (19) à s'engrener avec le pignon d'entrée en marche arrière (18) (pignon de sortie de marche arrière (17)).
PCT/JP2013/081972 2012-11-30 2013-11-27 Dispositif de changement de vitesse WO2014084282A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2012262165A JP2014109280A (ja) 2012-11-30 2012-11-30 シフト装置
JP2012-262165 2012-11-30

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Publication Number Publication Date
WO2014084282A1 true WO2014084282A1 (fr) 2014-06-05

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Families Citing this family (1)

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Publication number Priority date Publication date Assignee Title
JP6154150B2 (ja) * 2013-02-04 2017-06-28 アイシン・エーアイ株式会社 走行変速装置

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5385223A (en) * 1994-02-16 1995-01-31 Saturn Corporation Shift control mechanism for a multi-speed countershaft transmission
EP0694716A2 (fr) * 1994-07-25 1996-01-31 Saturn Corporation Mécanisme de changement de vitesse pour transmission à l'arbre secondaire de plusieurs vitesses
JP2012163178A (ja) * 2011-02-08 2012-08-30 Aisin Ai Co Ltd 変速機のリバースシフト装置

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Publication number Priority date Publication date Assignee Title
JPS5836426U (ja) * 1981-09-04 1983-03-09 トヨタ自動車株式会社 手動歯車変速機の変速操作機構
US5445253A (en) * 1994-02-16 1995-08-29 Saturn Corporation Shift control mechanism for a multi-speed countershaft transmission
JP3715209B2 (ja) * 2001-02-13 2005-11-09 本田技研工業株式会社 トランスミッション
JP5746555B2 (ja) * 2011-05-11 2015-07-08 アイシン・エーアイ株式会社 変速機におけるリバースシフト装置

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5385223A (en) * 1994-02-16 1995-01-31 Saturn Corporation Shift control mechanism for a multi-speed countershaft transmission
EP0668458A2 (fr) * 1994-02-16 1995-08-23 Saturn Corporation Dispositif de commande de changement de rapport pour une boîte de vitesse
JPH07259991A (ja) * 1994-02-16 1995-10-13 Saturn Corp トランスミッション用シフト制御機構
US5492209A (en) * 1994-02-16 1996-02-20 Saturn Corporation Shift control mechanism for a multi-speed countershaft transmission
EP0694716A2 (fr) * 1994-07-25 1996-01-31 Saturn Corporation Mécanisme de changement de vitesse pour transmission à l'arbre secondaire de plusieurs vitesses
JPH0861497A (ja) * 1994-07-25 1996-03-08 Saturn Corp 多速度中間軸トランスミッション用のシフト制御機構
US5560254A (en) * 1994-07-25 1996-10-01 Saturn Corporation Shift control mechanism for a multi-speed countershaft transmission
DE69515751T2 (de) * 1994-07-25 2000-07-20 Saturn Corp Schaltmechanismus für ein Mehrganggetriebe der Vorgelegebauart
JP2012163178A (ja) * 2011-02-08 2012-08-30 Aisin Ai Co Ltd 変速機のリバースシフト装置

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