WO2011027744A1 - 変速装置 - Google Patents
変速装置 Download PDFInfo
- Publication number
- WO2011027744A1 WO2011027744A1 PCT/JP2010/064796 JP2010064796W WO2011027744A1 WO 2011027744 A1 WO2011027744 A1 WO 2011027744A1 JP 2010064796 W JP2010064796 W JP 2010064796W WO 2011027744 A1 WO2011027744 A1 WO 2011027744A1
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- WO
- WIPO (PCT)
- Prior art keywords
- shaft
- shift
- output shaft
- electric motor
- driving force
- Prior art date
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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
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/26—Generation or transmission of movements for final actuating mechanisms
- F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
- F16H61/32—Electric motors actuators or related electrical control means therefor
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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
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/26—Generation or transmission of movements for final actuating mechanisms
- F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
- F16H2061/2838—Arrangements with single drive motor for selecting and shifting movements, i.e. one motor used for generating both movements
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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
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/26—Generation or transmission of movements for final actuating mechanisms
- F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
- F16H2061/2876—Racks
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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
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/26—Generation or transmission of movements for final actuating mechanisms
- F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
- F16H2061/2884—Screw-nut devices
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- 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
Definitions
- the present invention relates to a transmission that performs a shift operation and a select operation by a driving force of an electric motor.
- Each sleeve is engaged with one of a plurality of provided shift forks, and insertion / non-insertion of the corresponding sleeve is switched by driving the shift fork.
- a selection mechanism is provided for selecting the shift fork to be driven from a plurality of shift forks.
- the shift fork is driven by the driving force of an electric actuator typified by an air cylinder.
- Various transmission members are interposed between the electric actuator and the shift fork so that the driving force from the electric actuator can be transmitted to the shift fork, and the shift operation for driving the shift fork by the driving force of this electric actuator. Is done.
- the transmission is further provided with one electric actuator.
- Various transmission members are interposed between the electric actuator and the selection mechanism so that the driving force from the electric actuator can be transmitted to the selection mechanism.
- the driving force of the electric actuator is A select operation for selecting is performed.
- Patent Document 2 discloses an electric drive member that employs an electric motor instead of an electric actuator. In this configuration, the shift operation is performed by the rotational driving force of the first electric motor, and the selection operation is performed by the rotational driving force of the second electric motor.
- one of the objects of the present invention is to provide a transmission that can perform a shift operation and a select operation using the driving force of one electric motor.
- a transmission according to an aspect of the present invention includes an electric motor having a rotation shaft, a first output shaft that is provided coaxially with the rotation shaft of the electric motor, and a rotational driving force from the rotation shaft.
- a first electromagnetic clutch that transmits / cuts off to the first output shaft, a second output shaft that is provided coaxially with the rotary shaft, and a rotational driving force from the rotary shaft to the second output shaft;
- a rotational driving force of the electric motor applied to the first output shaft is used for a shift operation for driving a shift fork and applied to the second output shaft.
- the rotational driving force of the electric motor is used for a selection operation for selecting the shift fork to be driven.
- FIG. 2 is a cross-sectional view taken along section line II-II in FIG. It is sectional drawing which shows the structure of the shift / select drive device shown in FIG.
- FIG. 4 is a cross-sectional view taken along the cutting plane line IV-IV in FIG. 3.
- FIG. 6 is a sectional view taken along section line VI-VI in FIG. 5 (No. 1).
- FIG. 6 is a cross-sectional view taken along section line VI-VI in FIG. 5 (part 2).
- FIG. 1 is a diagram showing a schematic configuration of a transmission 1 according to one embodiment (first embodiment) of the present invention.
- 2 is a cross-sectional view taken along the cutting plane line II-II in FIG.
- the transmission 1 is mounted on a vehicle such as a passenger car or a truck, and includes a gear box 2.
- a main shaft (not shown) as an input shaft that receives input rotation from an engine or the like via a clutch (not shown), and extends parallel to the main shaft to a propeller shaft or the like.
- a counter shaft (not shown) is provided as an output shaft for transmitting the output rotation.
- a plurality of transmission gears are provided in the middle of each shaft.
- the transmission 1 employs a constant meshing system (constant mesh system), and the transmission gear of the main shaft and the transmission gear of the countershaft rotate all of which are always meshed.
- a transmission gear is attached to the counter shaft in an idle state.
- the shift forks 3 to 6 are fixed to fork shafts 7 to 10 that are associated one-to-one.
- the fork shafts 7 to 10 are provided so as to be movable parallel to each other and in the axial direction at a predetermined interval.
- a shift select shaft 11 extends in a direction perpendicular to the fork shafts 7 to 10 around the fork shafts 7 to 10 (above shown in FIG. 2).
- the shift select shaft 11 is rotatable about its axis and can be moved in the axial length direction.
- a shift lever 12 is fixed in the middle of the shift select shaft 11. The shift lever 12 can be selectively engaged with the fork shafts 7 to 10, and the shift lever 12 can be engaged with the fork shafts 7 to 10 by the rotation of the shift select shaft 11.
- the shift lever 12 includes a boss portion 13 fixed to the shift select shaft 11 and a projecting portion 14 projecting from the lower end of the boss portion 13.
- a shift / select drive device 21 for driving a shift operation and a select operation in the gear box 2 is attached to the peripheral surface (outer surface) of the gear box 2.
- One end side (the lower side shown in FIG. 1 and the right end side shown in FIG. 2) of the shift select shaft 11 protrudes out of the gear box 2 and enters the housing 22 of the shift / select drive device 21.
- FIG. 3 is a cross-sectional view showing the configuration of the shift / select drive device 21.
- FIG. 4 is a cross-sectional view taken along the cutting plane line IV-IV in FIG.
- the shift / select drive device 21 includes an electric motor 23 and a first conversion mechanism 24 for amplifying the rotational driving force of the electric motor 23 and converting it into a force for rotating the shift select shaft 11 about its central axis C1.
- a second conversion mechanism 25 for amplifying the rotational driving force of the electric motor 23 and converting the shift select shaft 11 into a force for moving the shift select shaft 11 in the axial length direction (left-right direction shown in FIG.
- the shift / select drive device 21 constitutes an electric actuator unit, and functions as a shift / select drive device when applied to the transmission 1 as shown in this embodiment.
- the eaves housing 22 has a bottomed cylindrical shape, and the opening (the left side shown in FIG. 3) of the housing 22 is closed by a plate-like lid 27.
- the housing 22 and the lid 27 are formed using a material such as cast iron or aluminum, for example, and the outer periphery of the lid 27 is fitted into the opening of the housing 22.
- the lid 27 is formed with a circular through hole 29 penetrating the inner surface (the right surface shown in FIG. 3) and the outer surface (the left surface shown in FIG. 3).
- the heel switching unit 26 is accommodated in a cylindrical accommodating portion 30 provided in the housing 22.
- a step portion 31 for receiving the switching unit 26 is formed at one end portion (the right end portion shown in FIG. 3) of the inner peripheral surface of the housing portion 30. In a state where the switching unit 26 is housed in a predetermined housing position in the housing portion 30, one end (the right end portion shown in FIG. 3) of the switching unit 26 and the step portion 31 are engaged.
- a shift select shaft 11 is supported in the bag housing 22 so as to be linearly reciprocable and rotatable in the axial direction (a direction perpendicular to the paper surface shown in FIG. 3; the left-right direction shown in FIG. 4).
- the shift select shaft 11 includes a first slide bearing 32 (see FIG. 4) fitted in a through hole 98 (see FIG. 4) formed in the housing 22, and the shift select shaft in the housing 22. 11 is supported by a second plain bearing 34 (see FIG. 4) fitted in the inner periphery of a bulging portion 33 (see FIG. 4) bulged so as to accommodate 11.
- a plurality of rack teeth 35 are formed in the axial direction on the peripheral surface of the heel shift select shaft 11.
- Each rack tooth 35 is provided relatively long in the circumferential direction so that the engagement between the rack tooth 35 and the pinion 36 (see FIG. 4) is maintained even when the shift select shaft 11 is rotated by a small amount.
- a spline portion 37 is formed at a predetermined position near the gear box 2 with respect to the rack teeth 35 on the peripheral surface of the shift select shaft 11.
- a brushless motor is employed as the electric motor 23.
- the electric motor 23 is disposed outside the housing 22.
- the electric motor 23 includes a cup-shaped motor housing 38, and a rotor (not shown) and a stator (not shown) accommodated in the motor housing 38.
- the electric motor 23 is provided with a motor driver (not shown), and the electric motor 23 is rotationally driven by driving the motor driver.
- An annular flange portion 39 projecting radially outward from the peripheral wall is formed at the base end portion (the right end portion shown in FIG. 3) of the peripheral wall of the motor housing 38. This flange portion 39 is fixed to the outer surface of the lid 27 (the left surface shown in FIG. 3).
- a rotating shaft 40 coaxially fixed to the rotor of the electric motor 23 extends along one direction (left-right direction shown in FIG. 3) orthogonal to the shift select shaft 11, and its tip projects out of the motor housing 38. (C2 shown in FIG. 3 is the rotation axis of the rotation shaft 40).
- the switching unit 26 includes a drive shaft 41 connected to the rotary shaft 40 of the electric motor 23 via a joint mechanism such as a spline joint, and one axial direction of the drive shaft 41 (the right side shown in FIG. 3).
- the first output shaft 42 is disposed coaxially with the first output shaft 42, is rotatably provided, an annular first electromagnetic clutch 43 that transmits / blocks the rotational driving force from the drive shaft 41 to the first output shaft 42, and the drive A second output shaft 44 that is rotatably provided coaxially with the shaft 41 and an annular second electromagnetic clutch 45 that transmits / cuts off the rotational driving force from the drive shaft 41 to the second output shaft 44 are provided.
- the drive shaft 41, the first output shaft 42, the first electromagnetic clutch 43, the second output shaft 44, and the second electromagnetic clutch 45 are accommodated in the unit housing 22.
- the drive shaft 41 includes a shaft body 46 that is coaxial with the rotary shaft 40 of the electric motor 23, and a large-diameter disk-shaped drive hub 47 that projects radially outward from the distal end portion of the shaft body 46. .
- the drive hub 47 is formed relatively thin.
- a disk-shaped first armature 48 is provided on one side of the drive hub 47 (the right side shown in FIG. 3). Further, a disc-shaped second armature 49 is disposed on the other side (left side shown in FIG. 3) of the drive hub 47.
- the first output shaft 42 has a substantially cylindrical shape, and is coaxially and rotatably provided on one side of the drive shaft 41 in the axial direction (the right side shown in FIG. 3). At the other end portion (left end portion shown in FIG. 3) of the first output shaft 42, a first output hub 50 is formed that protrudes radially outward from the cylindrical shaft body to form a large-diameter disk shape. ing.
- the first output hub 50 is arranged with a small gap from the first armature 48.
- the first electromagnetic coil 52 of the first electromagnetic clutch 43 is fitted on the outer periphery of the first output shaft 42 at a position adjacent to the first output hub 50.
- the first output hub 50 is sandwiched between the drive hub 47 (first armature 48) and the first electromagnetic coil 52.
- the first electromagnetic clutch 43 includes a first armature 48, a first output hub 50, and a first electromagnetic coil 52.
- the outer circumference of the first electromagnetic clutch 43 is fixed to the housing 22.
- the first output shaft 42 is supported by a first rolling bearing 51.
- the outer ring of the first rolling bearing 51 is fitted and fixed to the inner periphery of the first electromagnetic clutch 43. Further, the inner ring of the first rolling bearing 51 is externally fixed to the outer periphery of the first output shaft 42.
- the first electromagnetic clutch 43 When a DC voltage is applied to the first electromagnetic coil 52 of the first electromagnetic clutch 43, the first electromagnetic clutch 43 enters an operating state, and the first armature 48 is attracted to the first electromagnetic coil 52 and provided in the drive hub 47.
- the first armature 48 is connected to and connected to the other side surface (the left surface shown in FIG. 3) of the first output hub 50.
- the rotational driving force (rotational torque) on the drive hub 47 (drive shaft 41) side is transmitted to the first output shaft 42.
- the supply of the DC voltage to the first electromagnetic coil 52 is cut off, the connection between the first armature 48 and the first output hub 50 is released, and transmission of the rotational driving force to the first output shaft 42 ( Torque transmission) is cut off.
- a second output shaft 44 is provided coaxially with the first output shaft 42 so as to be rotatable on the side opposite to the first output shaft 42 with respect to the eaves driving hub 47. That is, the first and second output shafts 42 and 44 are arranged so as to sandwich the drive hub 47.
- the second output shaft 44 has a substantially annular shape and surrounds the drive shaft 41.
- the other end of the second output shaft 44 (the right end shown in FIG. 3) is formed with a second output hub 53 that protrudes radially outward from the annular shaft and forms a large-diameter disk. ing.
- the second output hub 53 is arranged with a minute gap from the second armature 49.
- a second electromagnetic coil 55 of the second electromagnetic clutch 45 is fitted on the outer periphery of the second output shaft 44 at a position adjacent to the second output hub 53.
- the second output hub 53 is sandwiched between the drive hub 47 (second armature 49) and the second electromagnetic coil 55.
- the second electromagnetic clutch 45 includes a second armature 49, a second output hub 53, and a second electromagnetic coil 55.
- the outer periphery of the second electromagnetic clutch 45 is fixed to the housing 22.
- the second output shaft 44 is supported by a second rolling bearing 54.
- the outer ring of the second rolling bearing 54 is fitted and fixed to the inner periphery of the second electromagnetic clutch 45. Further, the inner ring of the second rolling bearing 54 is externally fixed to the outer periphery of the second output shaft 44.
- the transmission efficiency of torque transmission from the drive shaft 41 to the first output shaft 42 can be kept large, and the torque from the drive shaft 41 to the second output shaft 44 can be maintained.
- the transmission efficiency of transmission can be kept large.
- the drive hub 47 is formed relatively thin, the distance between the first output shaft 42 and the second output shaft 44 does not become too large. Therefore, the axial length of the switching unit 26 can be kept short.
- the electromagnetic clutch mechanism including the first electromagnetic clutch 43 and the second electromagnetic clutch 45 is provided with a brake mechanism. Specifically, even when the second electromagnetic clutch 45 is in a non-operating state, that is, when the rotating shaft 40 and the second output shaft 44 are released, the second output shaft 44 is fixedly held by the electromagnetic clutch mechanism. Yes.
- a relatively small-diameter annular first gear (transmission mechanism) 56 is externally fixed to the outer periphery of the second output shaft 44 adjacent to one end side (the right side shown in FIG. 3) of the second rolling bearing 54.
- the first gear 56 is provided coaxially with the second output shaft 44.
- the first gear 56 is supported by a third rolling bearing 57.
- the outer ring of the third rolling bearing 57 is fitted and fixed to the inner periphery of the first gear 56.
- the inner ring of the third rolling bearing 57 is externally fitted and fixed to the outer periphery of the drive shaft 41.
- the drive shaft 41, the first and second output shafts 42, 44, the first gear 56, the first to third rolling bearings 51, 54, 57, and the first and second electromagnetic clutches 43, 45 are units. It has become. Therefore, when the transmission 1 is assembled, the members 41 to 45, 51, 54, 56, and 57 can be easily attached to the housing 22.
- the switching unit 26 When the switching unit 26 is mounted in the housing 22, when the switching unit 26 enters the housing portion 30 through the opening of the housing 22, one end of the switching unit 26 engages with the step portion 31. It is mounted at a predetermined storage position. As a result, the switching unit 26 can be easily mounted in the housing 22.
- the first conversion mechanism 24 includes a ball screw mechanism 58 and a connecting rod 60 that connects the nut 59 of the ball screw mechanism 58 and the shift select shaft 11.
- the ball screw mechanism 58 includes a screw shaft 61 connected to the first output shaft 42 and extending coaxially with the first output shaft 42, and a nut 59 attached to the screw shaft 61.
- the ball screw mechanism 58 converts the rotary motion of the first output shaft 42 into the axial linear motion of the nut 59.
- the scissor screw shaft 61 has a male thread in the entire region except for both ends thereof.
- the inner periphery of the nut 59 has a female screw (not shown).
- a plurality of balls (not shown) are interposed between the male screw of the screw shaft 61 and the female screw of the nut 59 so as to allow rolling.
- a first end 63 (left end shown in FIG. 3) of the screw shaft 61 is supported by a fourth rolling bearing 64.
- the inner ring of the fourth rolling bearing 64 is externally fitted and fixed to the first end 63 of the screw shaft 61. Further, the outer ring of the fourth rolling bearing 64 is fitted in the through hole 16 that penetrates the inner and outer surfaces of the bottom wall 65 of the unit housing 22.
- the outer ring of the fourth rolling bearing 64 is in contact with the annular step portion 66, and movement in one axial direction (leftward in FIG. 3) is restricted. Further, a lock nut 15 is engaged with the outer ring of the fourth rolling bearing 64, and movement in the other axial direction (rightward in FIG. 3) is restricted.
- the portion of the first end 63 of the screw shaft 61 that is closer to the electric motor 23 than the fourth rolling bearing 64 (left side shown in FIG. 3) is inserted into the inner periphery of the first output shaft 42, and this first output.
- the shaft 42 is connected to be integrally rotatable.
- a second end 68 (right end shown in FIG. 3) of the screw shaft 61 is supported by a fifth rolling bearing 67.
- the inner ring of the fifth rolling bearing 67 is externally fitted and fixed to the second end 68 of the screw shaft 61. Further, the outer ring of the fifth rolling bearing 67 is fixed in a cylindrical recess 69 formed in the bottom of the housing
- the nut 59 has a substantially rectangular parallelepiped shape. On both side surfaces of the nut 59, a pair of cylindrical shafts 70 (only one is shown in FIG. 3) extending in a direction parallel to the shift select shaft 11 (a direction perpendicular to the paper surface in FIG. 3; the left-right direction shown in FIG. 4). .) Projectingly formed.
- the connecting rod 60 is provided at a first end portion 72 (upper end portion in FIGS. 3 and 4), a first connecting portion 73 for connecting to the nut 59, and a second end portion 74 ( 3 and FIG. 4) and a second connecting portion 75 (see FIG. 4) for connecting to the shift select shaft 11.
- the first connecting portion 73 is, for example, a metal bracket, and connects the pair of support plate portions 76 and 76 to the base end portions of the support plate portions 76 and 76 (upper end portions in FIGS. 3 and 4).
- Connecting rod 77 (see FIG. 4), and in a side view, has a roll-over U-shape (a shape obtained by rolling the U-shape by 90 °).
- Each of the support plate portions 76 and 76 is formed with an axial U-shaped groove 78 cut out from the tip side (the upper end portion in FIGS. 3 and 4).
- the shaft 70 is engaged with the U-shaped groove 78.
- the groove width of the U-shaped groove 78 is set to a size that matches the diameter of the shaft 70, and is substantially uniform along the axial direction of the connecting rod 60.
- the nut 59 Since the flange shaft 70 and the U-shaped groove 78 are engaged, the nut 59 is provided so as to be rotatable around the shaft 70 with respect to the connecting rod 60. Further, since the engagement destination of the shaft 70 is the U-shaped groove 78, the engagement state between the shaft 70 and the U-shaped groove 78 is maintained even if the distance between the shaft 70 and the connecting rod 60 changes. be able to. Therefore, even when the nut 59 moves in the axial direction and the interval between the nut 59 and the shift select shaft 11 changes, the engaged state between the shaft 70 and the U-shaped groove 78 can be maintained. .
- the second connecting portion 75 has a cylindrical shape and is externally fitted to the shift select shaft 11.
- the second connecting portion 75 is formed with a spline groove 79 (see FIG. 4) that is spline-fitted to a spline portion 37 formed on the peripheral surface of the shift select shaft 11. Therefore, the second connecting portion 75 is connected to the shift select shaft 11 in a state in which relative rotation is impossible and relative axial movement is permitted. Therefore, the connecting rod 60 is provided so as to be swingable around the central axis C ⁇ b> 1 of the shift select shaft 11.
- the nut 59 moves along the axial direction (the left-right direction shown in FIG. 3; the direction perpendicular to the paper surface shown in FIG. 4) along with the rotation of the screw shaft 61, as shown in FIG. 60 swings around the central axis C ⁇ b> 1 of the shift select shaft 11.
- the second conversion mechanism 25 includes a first gear (transmission mechanism) 56, a transmission shaft (transmission mechanism) 95 that extends in parallel with the drive shaft 41, and a first end 80 ( 3) A second gear (transmission mechanism) 81 that is coaxially fixed at a predetermined position near the left end portion, and a predetermined position near the second end portion 82 (the right end portion shown in FIG. 3) of the transmission shaft 95. And a small-diameter pinion 36 fixed coaxially therewith.
- the first gear 56 and the second gear 81 are spur gears, respectively.
- the second gear 81 is formed with a larger diameter than both the first gear 56 and the pinion 36. That is, the second conversion mechanism 25 constitutes a speed reducer.
- the first end portion 80 (the left end portion shown in FIG. 3) of the rod transmission shaft 95 is supported by a sixth rolling bearing 96.
- the inner ring of the sixth rolling bearing 96 is externally fitted and fixed to the first end 80 (the left end shown in FIG. 3) of the transmission shaft 95.
- the outer ring of the sixth rolling bearing 96 is fixed in a cylindrical recess 83 formed on the inner surface of the lid 27 (the right surface shown in FIG. 3).
- the second end portion 82 (the right end portion shown in FIG. 3) of the transmission shaft 95 is supported by a seventh rolling bearing 84.
- the inner ring of the seventh rolling bearing 84 is externally fitted and fixed to the second end portion 82 of the transmission shaft 95.
- the outer ring of the seventh rolling bearing 84 is fixed in a cylindrical recess 86 formed around a sensor hole 85 (described below) at the bottom of the housing 22.
- the amount of rotation of the heel transmission shaft 95 is detected by a first rotation amount sensor 87.
- the bottom wall of the housing 22 is formed with a sensor hole 85 penetrating the inner and outer surfaces.
- the first rotation amount sensor 87 is disposed near the bottom of the housing 22 outside the housing 22, and the distal end portion of the first sensor shaft 99 extending from the sensor portion (not shown) passes through the sensor hole 85 and the transmission shaft 95.
- the second end portion 82 is connected to the second end portion 82 so as to be integrally rotatable.
- the rotation amount of the shift select shaft 11 is detected by the rotation of the first sensor shaft 99 accompanying the rotation of the shift select shaft 11.
- the detection value of the first rotation amount sensor 87 is input to the ECU 88 described later.
- a second rotation amount sensor 89 for detecting the rotation amount of the shift select shaft 11 is provided in the housing 22.
- the second rotation amount sensor 89 includes a main body 90 in which a sensor unit (not shown) is incorporated, a second sensor shaft 94 connected to the sensor unit, and a sector gear 91 that is externally fixed to the second sensor shaft 94. And.
- the sector gear 91 meshes with a sensor gear 92 that is externally fixed to the shift select shaft 11.
- the rotation amount of the shift select shaft 11 is detected by the rotation of the second sensor shaft 94 accompanying the rotation of the shift select shaft 11.
- the detection value of the second rotation amount sensor 89 is input to the ECU 88 described below.
- an ECU 88 Electronic Control Unit
- the ECU 88 drives and controls the electric motor 23 via a motor driver (not shown).
- the ECU 88 controls driving of the first and second electromagnetic clutches 43 and 45 through a relay circuit (not shown).
- the connecting rod 60 swings around the central axis C ⁇ b> 1 of the shift select shaft 11. Since the second connecting portion 75 of the connecting rod 60 is provided on the shift select shaft 11 so as not to rotate relatively, the shift select shaft 11 rotates as the connecting rod 60 swings.
- the second electromagnetic clutch 45 when the second electromagnetic clutch 45 is operated in a state where the electric motor 23 is rotationally driven and the rotational driving force from the electric motor 23 is applied to the second output shaft 44, the rotation of the second output shaft 44 is performed.
- the driving force is applied to the pinion 36 via the first gear 56, the second gear 81 and the transmission shaft 95.
- the shift select shaft 11 moves in the axial direction as the pinion 36 rotates due to the engagement of the rack teeth 35 and the pinion 36. In other words, the rotational driving force of the pinion 36 is converted into a moving force of the shift select shaft 11 in the axial direction.
- the shift select shaft 11 in the operating state of the first electromagnetic clutch 43, the shift select shaft 11 is rotationally driven, and in the operating state of the second electromagnetic clutch 45, the shift select shaft 11 moves in the axial direction. Accordingly, by selectively operating the first and second electromagnetic clutches 43 and 45, the shift operation and the select operation can be performed individually. Thus, the shift operation and the select operation can be performed using the driving force of one electric motor 23.
- the second output shaft 44 is formed in an annular shape, and the second output shaft is disposed so as to surround the drive shaft 41. Can be kept short. Thereby, the shift / select drive device 21 can be downsized, and the transmission 1 as a whole can be downsized. Furthermore, since the rotational driving force of the first output shaft 42 is converted into linear motion using the ball screw mechanism 58, the shift / select driving device 21 can be further miniaturized.
- FIG. 5 is a diagram showing a schematic configuration of a transmission 101 according to another embodiment (second embodiment) of the present invention.
- the same reference numerals as those in FIGS. 1 to 4 are attached to the portions corresponding to the respective parts shown in the embodiment of FIG. 1 to FIG. 4 (first embodiment). The description is omitted.
- the shift shaft 102 and the select operation for performing the shift operation are used instead of the shift select shaft 11 (see FIGS. 2 to 4) for performing the shift operation / select operation.
- a select shaft 103 is provided in the gear box 2 (see FIG. 1).
- the shift shaft 102 and the select shaft 103 extend in directions orthogonal to each other.
- a shift operation for driving the shift forks 3 to 6 (see FIG. 2) is performed by the rotation of the shift shaft 102 around the axis, and the shift shaft 102 is driven by the movement of the select shaft 103 in the axial direction.
- a selection operation for selecting the shift forks 3 to 6 is performed.
- One end portion (the lower portion shown in FIG. 5) of the shift shaft 102 protrudes out of the gear box 2 and reaches the peripheral region of the housing of the shift / select drive device 104 described below.
- one end side portion of the select shaft 103 (the portion on the front side in FIG. 5) protrudes out of the gear box 2.
- a shift / select driving device 104 for driving a shift operation and a select operation in the gear box 2 is attached to the peripheral surface (outer surface) of the gear box 2.
- a second end 144B (see FIG. 6A) of the first connecting rod 144 (see FIG. 6A) of the shift / select drive device 104 is fixed to the shift shaft 102.
- the first end 179A of the second link arm 179 of the link mechanism 106 is fixed to the select shaft 103.
- the link mechanism 106 connects the select shaft 103 and a second nut 172 of a second ball screw mechanism 170 (described later), and the rotational driving force of the electric motor 109 (described below) of the shift / select drive device 104. Is transmitted to the select shaft 103.
- the shift / select drive device 104 includes a first reduction gear unit 107, a second reduction gear unit 108, and an electric motor 109 sandwiched between the first reduction gear unit 107 and the second reduction gear unit 108. ing.
- the shift / select drive device 104 constitutes an electric actuator unit, and functions as a shift / select drive device when applied to the transmission 101 as shown in this embodiment. Since the shift / select drive device 104 has a structure in which the electric motor 109 is sandwiched between the first reduction gear unit 107 and the second reduction gear unit 108, the distance between the shift shaft 102 and the selection shaft 103 is small.
- the shift shaft 102 may not be directly connected to the first reduction gear unit 107, or the select shaft 103 may not be directly connected to the second reduction gear unit 108.
- the link mechanism 106 is used to link the select shaft 103 and the second reduction gear unit 108 together.
- FIG. 6A and 6B are cross-sectional views taken along section line VI-VI in FIG. 6A shows a cross-sectional configuration of the first reduction gear unit 107 and the electric motor 109
- FIG. 6B shows a cross-sectional configuration of the electric motor 109 and the second reduction gear unit 108.
- a brushless motor is employed as the electric motor 109.
- the electric motor 109 includes a motor housing 111 and a rotor 112 and a stator 113 accommodated in the motor housing 111.
- the rotor 112 has an annular shape, and a plurality of permanent magnets are held on the outer periphery thereof.
- the outer periphery of the rotor 112 is a magnetic pole in which the N pole and the S pole are alternately switched.
- a rotating shaft 114 is coaxially fixed to the rotor 112. The rotor 112 and the rotation shaft 114 can be rotated together (C2 in FIGS. 6A and 6B is the rotation axis of the rotation shaft 114).
- the motor housing 111 includes a cylindrical bracket 115 that surrounds the outer periphery of the stator 113, a substantially annular first cover bracket 116 that closes one end of the cylindrical bracket 115 (the right end shown in FIGS. 6A and 6B), and a substantially circular plate. And a second cover bracket 118 that closes the other end of the cylindrical bracket 115 (the left end shown in FIGS. 6A and 6B).
- the partition wall 117 partitions between the space in which the rotor 112 and the stator 113 are accommodated and the first reduction gear unit 107 side.
- a first end 119 (right end shown in FIG.
- the rotating shaft 114 protrudes from the partition wall 117 (motor housing 111), and a cylindrical first drive shaft 120 (described later) of the first reduction gear unit 107. .) Is fixed through the inner circumference. Further, the second end 121 (the left end shown in FIGS. 6A and 6B) of the rotation shaft 114 is inserted through the insertion hole 122 formed in the second cover bracket 118 and protrudes from the second cover bracket 118. Yes. The second end 121 of the rotary shaft 114 is fixed by being inserted through the inner periphery of a cylindrical second drive shaft 123 (described later) of the second reduction gear unit 108. That is, the rotating shaft 114 passes through the motor housing 111.
- the rotor 112 and the rotating shaft 114 are rotatably supported by the eighth rolling bearing 124.
- the inner ring of the eighth rolling bearing 124 is externally fitted and fixed to the outer periphery of the second end 121 of the rotating shaft 114. Further, the outer ring of the eighth rolling bearing 124 is fitted into the inner periphery of the insertion hole 122.
- the cylindrical bracket 115 is fixed to the first cover bracket 116 by bolts 125 and is fixed to the second cover bracket 118 by bolts 126.
- the first cover bracket 116 is fixed to the first unit housing 132 of the first reduction gear unit 107 by bolts 127, and the second cover bracket 118 is the second unit of the second reduction gear unit 108 by bolts 128. It is fixed to the housing 157. Thereby, the fixing of the motor housing 111 to the first unit housing 132 and the second unit housing 157 is achieved.
- the first reduction gear unit 107 includes a first drive shaft 120 coupled to a first end portion 119 (a right end portion shown in FIG. 6A) of the rotation shaft 114 of the electric motor 109 so as to be integrally rotatable, and the first drive shaft 120.
- the cylindrical first output shaft 129 is coaxially disposed on the opposite side to the electric motor 109 side (the right side shown in FIG. 6A) and is rotatably provided, and the rotational drive force from the first drive shaft 120. Is transmitted to and cut off from the first output shaft 129, and the rotational driving force applied to the first output shaft 129 from the electric motor 109 is amplified, and the shift shaft 102 is rotated around its axis.
- a third conversion mechanism 131 for converting to a rotating force.
- the first drive shaft 120, the first output shaft 129, the first electromagnetic clutch 130, and the third conversion mechanism 131 are accommodated in the first unit housing 132.
- the first unit housing 132 includes a substantially cylindrical first tube portion 133 and a first lid 134 that closes one end portion (the right end portion shown in FIG. 6A) of the first tube portion 133.
- the first lid 134 is fixed to the first tube portion 133 with bolts 135.
- a first passage hole 146 for allowing a first connection rod (connection rod) 144 of a first ball screw mechanism (ball screw mechanism) 142 (described later) to pass therethrough is provided in the central portion of the first tube portion 133 in the axial direction. Is formed.
- the first drive shaft 120 has a substantially cylindrical shape and extends coaxially with the rotation shaft 114 of the electric motor 109.
- the first drive shaft 120 has a substantially cylindrical inner periphery on which the rotation shaft 114 of the electric motor 109 is inserted and fixed.
- a large-diameter disk-shaped first drive hub 136 is provided in the axial center of the first drive shaft 120.
- a first armature 137 is disposed on the peripheral edge of the first drive hub 136 on one side (the right side shown in FIG. 6A).
- the first output shaft 129 is coaxially and rotatably provided on one axial side of the first drive shaft 120 (the right side shown in FIG. 6A).
- a first output hub 138 having a large-diameter disk projecting outward in the radial direction is formed at one end of the first output shaft 129 (the right end shown in FIG. 6A).
- the first output hub 138 is disposed with a small gap from the first armature 137.
- the first electromagnetic coil 141 of the first electromagnetic clutch 130 is fitted on the outer periphery of the first output shaft 129 at a position adjacent to the first output hub 138. In other words, the first output hub 138 is sandwiched between the first drive hub 136 (first armature 137) and the first electromagnetic coil 141.
- the first electromagnetic clutch 130 includes a first armature 137, a first output hub 138, and a first electromagnetic coil 141.
- the outer periphery of the first electromagnetic clutch 130 is fixed to the first unit housing 132.
- the first output shaft 129 is supported by a ninth rolling bearing 139 and a tenth rolling bearing 140.
- the outer ring of the ninth rolling bearing 139 is fitted and fixed to a step formed on the inner surface of the first output shaft 129.
- the inner ring of the ninth rolling bearing 139 is fitted and fixed to the outer periphery of the first drive shaft 120.
- the outer ring of the tenth rolling bearing 140 is fitted and fixed to the inner periphery of the first electromagnetic clutch 130. Further, the inner ring of the tenth rolling bearing 140 is externally fitted and fixed to the outer periphery of the first output shaft 129.
- the first electromagnetic clutch 130 When a DC voltage is applied to the first electromagnetic coil 141 of the first electromagnetic clutch 130, the first electromagnetic clutch 130 enters an operating state, and the first armature 137 is attracted to the first electromagnetic coil 141, and the first drive hub 136. A first armature 137 provided on the first output hub 138 is connected to the first armature 137. Thus, the torque on the first drive hub 136 (first drive shaft 120) side is transmitted to the first output shaft 129.
- the supply of the DC voltage to the first electromagnetic coil 141 is cut off, the connection between the first armature 137 and the first output hub 138 is released, and the first drive hub 136 (first drive shaft 120) is disconnected. Torque transmission to the first output shaft 129 is cut off.
- the third conversion mechanism 131 includes a first ball screw mechanism 142 and a first connection rod 144 that connects the first nut (nut) 143 of the first ball screw mechanism 142 and the shift shaft 102.
- the first ball screw mechanism 142 is connected to the first output shaft 129 so as to be integrally rotatable, and is attached to the first screw shaft 145 and a first screw shaft (screw shaft) 145 extending coaxially with the first output shaft 129.
- a first nut 143 The first ball screw mechanism 142 converts the rotational movement of the first output shaft 129 into the axial linear movement of the first nut 143.
- the first screw shaft 145 has a male screw in the whole area excluding both ends.
- the inner periphery of the first nut 143 has a female screw (not shown).
- a plurality of balls (not shown) are interposed between the male screw of the first screw shaft 145 and the female screw of the first nut 143 so as to allow rolling.
- a first end 147 (left end shown in FIG. 6A) of the first screw shaft 145 is inserted into the inner periphery of the first output shaft 129 and is coupled to the first output shaft 129 so as to be integrally rotatable. .
- a second end 148 (the right end shown in FIG. 6A) of the first screw shaft 145 is supported by an eleventh rolling bearing 149.
- the inner ring of the eleventh rolling bearing 149 is externally fixed to the second end 148 of the first screw shaft 145. Further, the outer ring of the eleventh rolling bearing 149 is fixed in a cylindrical recess 150 formed on the inner surface (the right surface shown in FIG. 6A) of the first lid 134.
- the first nut 143 has a substantially rectangular parallelepiped shape. On both side surfaces of the first nut 143, a pair of cylindrical shafts 151 (only one is shown in FIG. 6A) extending in a direction parallel to the shift shaft 102 (a direction perpendicular to the paper surface in FIG. 6A) are formed to protrude. ing. A first connecting portion 152 for connecting to the first nut 143 is provided at the first end portion 144A (the upper end portion in FIG. 6A) of the first connecting rod 144. Moreover, the 2nd end part 144B (the lower end part in FIG. 3 and FIG. 4) of the 1st connection rod 144 is being fixed to the shift shaft 102 (it is provided so that relative rotation is impossible).
- the connecting portion 152 has the same structure as the first connecting portion 73 of the connecting rod 60 shown in FIGS. 3 and 4, and includes a pair of support plate portions 153 (only one is shown in FIG. 6A) and each support plate portion 153. And connecting rods (not shown) that connect the base ends of each of them (upper end in FIG. 6A).
- the connecting portion 152 has a roll-over U-shape (a shape obtained by rolling the U-shape by 90 °) in a side view.
- Each of the support plate portions 153 and 153 is formed with a U-shaped groove 154 that is cut out from the distal end side (the upper end portion in FIG.
- each support plate portion 153 has a proximal end portion. It has a bifurcated fork shape that extends from the tip toward the tip.
- a shaft 151 is engaged with the U-shaped groove 154.
- the groove width of the U-shaped groove 154 is set to a size that matches the diameter of the shaft 151 and is substantially uniform along the axial direction of the first connecting rod 144.
- the first nut 143 Since the flange shaft 151 and the U-shaped groove 154 are engaged, the first nut 143 is provided so as to be rotatable around the shaft 151 with respect to the first connecting rod 144. Further, since the engagement destination of the shaft 151 is the U-shaped groove 154, the engagement state between the shaft 151 and the U-shaped groove 154 is changed even if the distance between the shaft 151 and the first connecting rod 144 is changed. Can keep. Therefore, even when the first nut 143 moves in the axial direction and the distance between the first nut 143 and the shift shaft 102 changes, the engagement state between the shaft 151 and the U-shaped groove 154 is maintained. be able to.
- the second reduction gear unit 108 has a second drive shaft 123 fixed to the second end 121 (the left end shown in FIG. 6B) of the rotating shaft 114 of the electric motor 109, and the second drive shaft 123.
- the second output shaft 158 is coaxially disposed on the side opposite to the electric motor 109 side (the left side shown in FIG. 6B) and is rotatably provided, and the rotational drive force from the second drive shaft 123 is the second output shaft.
- An annular second electromagnetic clutch 159 that transmits / blocks to 158, and the rotational driving force applied to the second output shaft 158 from the electric motor 109 is amplified and converted to a force that rotates the shift shaft 102 about its axis.
- a fourth conversion mechanism 156 The second drive shaft 123, the second output shaft 158, the second electromagnetic clutch 159, and the fourth conversion mechanism 156 are accommodated in the second unit housing 157.
- the second unit housing 157 includes a substantially cylindrical second tube portion 160 and a second lid 161 that closes the other end portion (the left end portion shown in FIGS. 6A and 6B) of the second tube portion 160. Yes.
- the second lid 161 is fixed to the second cylinder portion 160.
- a second passage hole 163 for allowing the first link arm 178 of the link mechanism 106 to pass therethrough is formed in the central portion of the second cylindrical portion 160 in the axial direction.
- the second passage hole (not shown) is formed at a position that intersects the first passage hole 135 by 90 ° when viewed from the extension line of the rotating shaft 114.
- the second drive shaft 123 has a substantially cylindrical shape and extends coaxially with the rotation shaft 114 of the electric motor 109.
- the rotation shaft 114 of the electric motor 109 is inserted and fixed to the inner periphery of the second drive shaft 123 in a substantially cylindrical shape.
- a large-diameter disk-shaped second drive hub 164 is provided at the axial center of the second drive shaft 123.
- a second armature 165 is disposed on the peripheral edge of the second drive hub 164 on the other side (left side shown in FIG. 6B).
- the second output shaft 158 is coaxially and rotatably provided on the other side of the second drive shaft 123 (left side shown in FIG. 6B).
- a second output hub 166 having a large-diameter disk shape protruding outward in the radial direction is formed at one end of the second output shaft 158 (the left end shown in FIG. 6B).
- the second output hub 166 is disposed with a small gap from the second armature 165.
- a second electromagnetic coil 169 of the second electromagnetic clutch 159 is fitted on the outer periphery of the second output shaft 158 at a position adjacent to the second output hub 166.
- the second output hub 166 is sandwiched between the second drive hub 164 (second armature 165) and the second electromagnetic coil 169 of the second electromagnetic clutch 159.
- the second electromagnetic clutch 159 includes a second armature 165, a second output hub 166, and a second electromagnetic coil 169.
- the outer periphery of the second electromagnetic clutch 159 is fixed to the second unit housing 157.
- the second output shaft 158 is supported by a twelfth rolling bearing 167 and a thirteenth rolling bearing 168.
- the outer ring of the twelfth rolling bearing 167 is internally fitted and fixed to a step portion formed on the inner surface of the second output shaft 158.
- the inner ring of the twelfth rolling bearing 167 is fixed by being fitted on the outer periphery of the second drive shaft 123.
- the outer ring of the thirteenth rolling bearing 168 is fitted and fixed to the inner periphery of the second electromagnetic clutch 159. Further, the inner ring of the thirteenth rolling bearing 168 is externally fitted and fixed to the outer periphery of the second output shaft 158.
- the fourth conversion mechanism 156 includes a second ball screw mechanism 170.
- the second ball screw mechanism 170 includes a second screw shaft 171 connected to the second output shaft 158 and extending coaxially with the second output shaft 158, and a second nut 172 attached to the second screw shaft 171. Yes.
- the second ball screw mechanism 170 converts the rotational motion of the second output shaft 158 into the linear motion of the second nut 172 in the axial direction.
- the second screw shaft 171 has a male screw in the whole area except for both ends.
- the inner periphery of the second nut 172 has a female screw (not shown).
- a plurality of balls (not shown) are interposed between the male screw of the second screw shaft 171 and the female screw of the second nut 172 so as to allow rolling.
- the first end 173 (the right end shown in FIG. 6B) of the second screw shaft 171 is inserted through the inner periphery of the second output shaft 158 and connected to the second output shaft 158 so as to be integrally rotatable. .
- a second end 174 (left end shown in FIG. 6B) of the second screw shaft 171 is supported by a fourteenth rolling bearing 175.
- the inner ring of the fourteenth rolling bearing 175 is externally fitted and fixed to the second end 174 (the left end shown in FIG. 6B) of the second screw shaft 171. Further, the outer ring of the fourteenth rolling bearing 175 is fixed in a cylindrical recess 176 formed on the inner surface (the left surface shown in FIG. 6A) of the second lid 161.
- the second nut 172 has a substantially rectangular parallelepiped shape. On both side surfaces of the second nut 172, a pair of cylindrical shafts 177 and 177 extending in a direction parallel to the shift shaft 102 (up and down direction in FIG. 6B) are formed to project. A first link arm 178 (see FIG. 5) of the link mechanism 106 (see FIG. 5) is connected to the second nut 172 of the second ball screw mechanism 170.
- the link mechanism 106 includes a first link arm 178 having a first end 178A and a second end 178B, and a second link having a first end 179A and a second end 179B.
- An arm 179 and a third link arm 180 having a first end 180A and a second end 180B are provided.
- a connecting portion 181 for connecting to the second nut 172 is provided at the first end 178 ⁇ / b> A of the first link arm 178.
- the connecting portion 181 is engaged with the second nut 172.
- the first link arm 178 is provided to be rotatable around a fulcrum 182 provided on the outer surface of the gear box 2.
- the connecting portion 181 has the same structure as the first connecting portion 73 of the connecting rod 60 shown in FIGS. 3 and 4 and the connecting portion 152 of the first connecting rod 144 shown in FIG. 6A, and a pair of support plate portions 183, A connecting rod (not shown) for connecting the base end portions of each support plate portion 183 is provided.
- the connecting portion 181 has a U-shaped roll shape (a shape obtained by rolling the U shape by 90 °) in a side view.
- Each of the support plate portions 183 and 183 is formed with a U-shaped groove 184 that is cut out from the distal end side and extends in the axial direction.
- Each support plate portion 183 is bifurcated from the proximal end portion toward the distal end portion. It has a fork shape.
- a shaft 177 is engaged with the U-shaped groove 184.
- the groove width of the U-shaped groove 184 is set to a size that matches the diameter of the shaft 177, and is substantially uniform along the direction in which the first
- the second nut 172 Since the flange shaft 177 and the U-shaped groove 184 are engaged, the second nut 172 is provided so as to be rotatable around the shaft 177 with respect to the first link arm 178. Further, since the engagement destination of the shaft 177 is the U-shaped groove 184, the engagement state between the shaft 177 and the U-shaped groove 154 is changed even if the distance between the shaft 177 and the first link arm 178 is changed. Can keep. Therefore, even when the second nut 172 moves in the axial direction and the distance between the second nut 172 and the second link arm 179 changes, the engagement state between the shaft 177 and the U-shaped groove 184 is maintained. Can keep.
- the first end 179A of the second link arm 179 is fixed to the select shaft 103, and the second link arm 179 is provided so as to be swingable around the central axis C4 of the select shaft 103.
- the third link arm 180 connects the second end 178B of the first link arm 178 and the second end 179B of the second link arm 179.
- the first end 180A of the third link arm 180 is connected to the second end 178B of the first link arm 178 via the first ball joint 185, and the third link arm 180
- the two end portions 180B are connected to the second end portion 179B of the second link arm 179 via the second ball joint 186. Therefore, the attitude of the third link arm 180 relative to the first link arm 178 and the second link arm 179 can be changed.
- the third link arm 180 swings around the select shaft 103.
- first and second drive shafts 120 and 123 rotate.
- the first and second electromagnetic clutches 130 and 159 are in the non-operating state, the first and second drive shafts 120 and 123 idle, and the driving force of the electric motor 109 is the first and second output shafts 129. , 158.
- the first electromagnetic clutch 130 is operated and the rotational driving force from the electric motor 109 is applied to the first output shaft 129, the first screw shaft 145 rotates with the rotation of the first output shaft 129.
- the first nut 143 attached to the first screw shaft 145 moves in the axial direction.
- the first connecting rod 144 swings around the central axis C3 of the shift shaft 102. Since the second end 144B of the first connecting rod 144 is fixed to the shift shaft 102, the shift shaft 102 rotates as the first connecting rod 144 swings.
- the second electromagnetic clutch 159 when the second electromagnetic clutch 159 is operated and the rotational driving force from the electric motor 109 is applied to the second output shaft 158, the second screw shaft 171 rotates with the rotation of the second output shaft 158.
- the second nut 172 attached to the second screw shaft 171 moves in the axial direction.
- the first link arm 178 of the link mechanism 106 swings around the fulcrum 182, and accordingly, the third link arm 180 moves around the central axis C 4 of the select shaft 103. Swing. Since the first end 180A of the third link arm 180 is fixed to the select shaft 103, the select shaft 103 rotates as the third link arm 180 swings.
- the shift shaft 102 when the first electromagnetic clutch 130 is in an operating state, the shift shaft 102 is rotationally driven, and when the second electromagnetic clutch 159 is in an operating state, the select shaft 103 is rotationally driven. Therefore, the shift operation and the select operation can be performed individually by selectively operating the first and second electromagnetic clutches 130 and 159. Thereby, the shift operation and the select operation can be performed using the driving force of one electric motor 109.
- the rotation shaft 114 extends through the motor housing 111, the first drive shaft 120 is coupled to the first end 119 of the rotation shaft 114 so as to be integrally rotatable, and the second rotation shaft 114 is connected to the second end 119.
- the second drive shaft 123 is coupled to the end portion 121 so as to be integrally rotatable.
- a first output shaft 129 is disposed on the opposite side of the first drive shaft 120 from the electric motor 109 side, and the first drive shaft 120 and the first output shaft 129 are connected via the first electromagnetic clutch 130. Connected.
- a second output shaft 158 is disposed on the opposite side of the electric motor side with respect to the second drive shaft 123, and the second drive shaft 123 and the second output shaft 158 are connected via the second electromagnetic clutch 19. Is done. Therefore, the configuration of the shift / select drive device 104 can be simplified.
- the first ball screw mechanism 142 is used to convert the rotational driving force of the first output shaft 129 into linear motion
- the second ball screw mechanism 170 is used to convert the rotational driving force of the second output shaft 158 in the linear direction. Since it is converted into motion, the shift / select drive device 104 can be downsized, and the transmission 101 as a whole can be downsized.
- the shift shaft 102 and / or the select shaft 103 may be provided with a rotation amount sensor for detecting the rotation amount of the shafts 102 and 103. .
- This rotation amount sensor detects, for example, the amount of movement of the first nut 143 (second nut 172) in the axial direction, and detects the amount of rotation of the shift shaft 102 and the select shaft 103 based on this. Good.
- FIG. 7A is a diagram showing a configuration of the shift / select drive device 202 of the transmission 201 according to the third embodiment of the present invention.
- FIG. 7B is a diagram viewed from an arrow VII in FIG. 7A.
- the parts corresponding to those shown in the embodiment (second embodiment) shown in FIGS. 5, 6A and 6B are the same as those shown in FIGS. 5, 6A and 6B.
- the reference numerals are attached and the description is omitted.
- a shift shaft 102 for performing a shift operation is placed in the gear box 2 (see FIG. 1).
- a select shaft 103 for performing a select operation is placed in the gear box 2 (see FIG. 1).
- the shift shaft 102 and the select shaft 103 extend in directions orthogonal to each other.
- a shift / select drive device 202 for driving a shift operation and a select operation in the gear box 2 is attached to the peripheral surface (outer surface) of the gear box 2.
- a first worm gear 206 of a shift / select drive device 202 is fixedly connected to the shift shaft 102.
- a second worm gear 208 of the shift / select driving device 202 is fixedly connected to the select shaft 103.
- the shift / select drive device 202 of the transmission 201 according to the third embodiment is different from the shift / select drive device 104 according to the second embodiment in that ball screw mechanisms 142 and 170 and a connecting rod 144 are provided.
- a third conversion mechanism 203 and a fourth conversion mechanism 204 having worm shafts 205, 207 and worm gears 206, 208 meshing with the worm shafts 205, 207 are provided. This is the point.
- a first worm shaft 205 extending coaxially with the first output shaft 129 is connected to one end portion of the first output shaft 129 (the right side portion shown in FIGS. 7A and 7B).
- the first worm shaft 205 meshes with the first worm gear 206.
- the first worm gear 206 is fixed coaxially with the shift shaft 102 (provided not to be relatively rotatable).
- the first worm gear 206 is constituted by a sector gear, for example.
- a second worm shaft 207 extending coaxially with the second output shaft 158 is connected to one end of the second output shaft 158 (the right side portion shown in FIGS. 7A and 7B).
- the second worm shaft 207 meshes with the second worm gear 208.
- the second worm gear 208 is fixed coaxially with the select shaft 103 (is provided so as not to be relatively rotatable).
- the second worm gear 208 is constituted by a sector gear, for example.
- the first electromagnetic clutch 130 When the first electromagnetic clutch 130 is operated in a state in which the electric motor 109 is rotationally driven and the rotational driving force from the electric motor 109 is applied to the first output shaft 129, the first output shaft 129 is rotated. As a result, the first worm shaft 205 rotates. As the first worm shaft 205 rotates, the first worm gear 206 rotates about the central axis C ⁇ b> 3 of the shift shaft 102. Since the first worm gear 206 is fixed coaxially with the shift shaft 102, the shift shaft 102 rotates as the first worm gear 206 rotates.
- the second electromagnetic clutch 159 when the second electromagnetic clutch 159 is operated in a state where the electric motor 109 is rotationally driven and the rotational driving force from the electric motor 109 is applied to the second output shaft 158, the rotation of the second output shaft 158 is performed. Accordingly, the second worm shaft 207 rotates. As the second worm shaft 207 rotates, the second worm gear 208 rotates around the central axis C4 of the select shaft 103. Since the second worm gear 208 is fixed coaxially with the select shaft 103, the select shaft 103 rotates as the second worm gear 208 rotates.
- the shift shaft 102 when the first electromagnetic clutch 130 is in an operating state, the shift shaft 102 is rotationally driven, and when the second electromagnetic clutch 159 is in an operating state, the select shaft 103 is rotationally driven. Therefore, the shift operation and the select operation can be performed individually by selectively operating the first and second electromagnetic clutches 130 and 159. Thereby, the shift operation and the select operation can be performed using the driving force of one electric motor 109.
- the shift shaft 102 and / or the select shaft 103 may rotate in an unintended direction due to reverse input. However, the meshing between the first worm shaft 205 and the first worm gear 206 and / or the second worm shaft 207 may occur. And the second worm gear 208 are locked by meshing, so that unintended rotation of the shift shaft 102 and / or the select shaft 103 can be prevented.
- FIG. 8 is a cross-sectional view showing the configuration of the shift / select drive device 250 of the transmission according to the fourth embodiment of the present invention.
- FIG. 9 is a diagram showing the configuration of the second gear shown in FIG. 8 and its surroundings. In FIG. 9, only the shift select shaft 11 and the second gear 251 are shown, and the other members are not shown (the first gear 56 is shown by a two-dot chain line).
- parts corresponding to those shown in the embodiment (first embodiment) shown in FIGS. 1 to 4 are denoted by the same reference numerals as those in the first embodiment, and will be described. Is omitted.
- a second gear 81 made of a sector gear is used instead of the second gear 81 made of a spur gear.
- the gear (transmission mechanism) 251 is provided.
- the second gear 251 is in mesh with the first gear 56.
- the shift select shaft 11 extends in the up-down direction (vertical direction or a direction close to the vertical direction) as shown in FIG. Since the transmission shaft 95 extends in a direction orthogonal to the shift select shaft 11, the transmission shaft 95 extends in the left-right direction (horizontal direction or a direction close to horizontal).
- the second gear 251 is attached to the transmission shaft 95 so as to be integrally rotatable.
- the second gear 251 has a semicircular shape.
- the second gear 251 has the same diameter as the second gear 81. Therefore, the first gear 56 and the second gear 251 constitute a part of the speed reducer.
- shift select shaft own weight rotational force (illustrated by a dotted line in FIG. 9) acts on the transmission shaft 95.
- the second electromagnetic clutch 45 When the second electromagnetic clutch 45 is in an operating state, that is, when the rotary shaft 40 and the second output shaft 44 are connected, the shift select shaft 11 is lowered (moved in the axial direction) by its own weight. Absent. However, in this embodiment, the second output shaft 44 is not provided with a brake mechanism or the like.
- the second electromagnetic clutch 45 when the second electromagnetic clutch 45 is in a non-operating state, that is, when the rotary shaft 40 and the second output shaft 44 are released, the rotary shaft 40 receives the rotational force of the shift select shaft and rotates. Therefore, there is a possibility that the shift select shaft 11 is allowed to descend.
- the shift select shaft 11 rotates, the axial position (select position) of the shift select shaft 11 may change without being controlled by the ECU 88.
- the first and second gears 56 and 251 constitute (a part of) the reduction gear, and the shift amount of the shift select shaft 11 required for the select operation is relatively small.
- the second gear 251 only needs to reciprocate within a certain angle to rotate. 9, when the second gear 251 is attached to the transmission shaft 95 in such a posture that the curved portion (arc) of the second gear 251 faces the side (the first gear 56 side), The position of the center of gravity of the second gear 251 is displaced in the radial direction from the rotational axis of the transmission shaft 95, and the rotational force due to the weight of the second gear 251 (hereinafter referred to as the “second gear self-weight rotational force”, shown by the solid line in FIG. 9). Acts on the transmission shaft 95.
- the second gear self-weight rotational force is set to a direction and magnitude that cancels the shift-select shaft self-weight rotational force. Therefore, the shift select shaft self-weight rotational force is canceled and the transmission shaft 95 does not rotate. Accordingly, it is possible to reliably prevent the shift select shaft 11 from being lowered when the rotary shaft 40 and the second output shaft 44 are released. As a result, it is possible to prevent the shift select shaft 11 from being lowered without employing an electromagnetic clutch or the like equipped with a brake mechanism, thereby preventing an increase in cost.
- the magnitude and direction of the second gear self-weight rotational force are set by selecting the number of teeth and / or weight of the second gear 251 and adjusting the mounting posture of the second gear 251 on the transmission shaft 95. Yes.
- the entire shift / select driving device 250 can be reduced in weight and space.
- the case where the second gear (sector gear) 251 has a semicircular shape has been described as an example.
- a sector gear having a fan shape may be used as the second gear. .
- a sector gear can be employed as the first gear.
- the second gear may be a spur gear or a sector gear.
- the shift-select shaft self-weight rotational force is set to a direction and magnitude that cancels the shift-select shaft self-weight rotational force, the shift-select shaft self-weight rotational force is canceled and the transmission shaft 95 does not rotate. Accordingly, it is possible to reliably prevent the shift select shaft 11 from being lowered when the rotary shaft 40 and the second output shaft 44 are released.
- the sixth rolling bearing 96 is arranged along the axial direction of the transmission shaft 95 (the left-right direction shown in FIG. 3). Further, an urging member (for example, a leaf spring) that presses elastically may be interposed. Since the transmission shaft 95 is pressed in the axial direction, the dimensional accuracy in the mounted state of the transmission shaft 95 can be improved.
- an urging member for example, a leaf spring
- the select shaft 103 and the second reduction gear unit 108 are interlocked using the link mechanism 106.
- the shift shaft 102 and the first reduction gear unit 107 are linked using the link mechanism 106. It can also be set as the structure linked with.
- the select shaft 103 and the second reduction gear unit 108 when the select shaft 103 and the second reduction gear unit 108 are directly connected, the first end is connected to the second nut 172 and the second end is fixed to the select shaft.
- the second connecting rod can be provided (connected so as not to be relatively rotatable).
- a connecting portion for connecting to the second nut 172 is provided at the first end of the second connecting rod. This connecting portion has the same configuration as the connecting portion 181 shown in the second embodiment, and engages with the second nut 172.
- the shift / select drive device 21 of the first embodiment can be used for rotational driving of the shift shaft 102 and the select shaft 103 as shown in the second and third embodiments, and the second and third.
- the shift / select drive devices 104 and 202 of the embodiment can also be used for rotation and axial movement of the shift select shaft 11 as shown in the first embodiment.
- various design changes can be made within the scope of matters described in the claims.
- the transmission (1; 101; 201) is provided to be rotatable coaxially with the electric motor (23; 109) having a rotating shaft (40; 114) and the rotating shaft of the electric motor.
- the first output shaft (42; 129), the first electromagnetic clutch (43; 130) for transmitting / cutting off the rotational driving force from the rotating shaft to the first output shaft, and the first output shaft (42; 129) can rotate coaxially with the rotating shaft.
- a second output shaft (44; 158) provided on the first output shaft, and a second electromagnetic clutch (45; 159) for transmitting / cutting off the rotational driving force from the rotary shaft to the second output shaft.
- the rotational driving force of the electric motor applied to the output shaft is used for a shift operation for driving the shift forks (3 to 6), and the rotational driving force of the electric motor applied to the second output shaft is ,
- the shift force to be driven This is used for a select operation for selecting a key (3 to 6).
- the transmission according to the embodiment of the present invention includes an electric motor (23) having a rotation shaft (40), and a drive that is provided coaxially with the rotation shaft of the electric motor and is rotationally driven by the rotational driving force of the electric motor.
- a second electromagnetic clutch (45) for shutting off wherein the second output shaft forms an annular shape and surrounds the drive shaft, and the first output shaft includes the drive shaft and the second output shaft.
- the rotational driving force of the electric motor applied to one output shaft is used to select a shift operation for driving the shift fork (3 to 6) and the shift fork (3 to 6) to be driven. It is used for one of the selection operations, and the rotational driving force of the electric motor applied to the second output shaft is used for the other of the shift operation and the selection operation.
- the shift operation and the select operation can be performed individually by selectively operating the first and second electromagnetic clutches.
- the shift operation and the select operation can be performed using the rotational driving force of one electric motor.
- two electromagnetic clutches may be arranged along the axial direction of the rotating shaft of the electric motor.
- first clutch and second clutch may be arranged along the axial direction of the rotating shaft of the electric motor.
- a complicated transmission mechanism is required, and the structure including the drive shaft, the first and second output shafts, and the first and second electromagnetic clutches may be complicated. Since the two electromagnetic clutches extend along the axial direction of the rotating shaft, the apparatus may be increased in size.
- the second output shaft can be disposed so as to surround the periphery of the drive shaft by forming the second output shaft in an annular shape. Therefore, the axial length required for the combination of the drive shaft, the first output shaft, and the second output shaft can be shortened, and thereby the apparatus can be reduced in size.
- the drive shaft includes a shaft body (46) and a drive hub (47) projecting radially outward from the shaft body, and the first and second output shafts are connected to the drive shaft. It is preferable to arrange them with the hub in between. In this case, the transmission efficiency of torque transmission from the drive shaft to the first and second output shafts can be kept large while downsizing the device.
- a transmission (101; 201) includes a motor housing (111), an electric motor (109) having a rotation shaft (114) extending through the motor housing, and the rotation shaft.
- 2nd output provided coaxially with the shaft (158) and a second electromagnetic clutch (159) for transmitting / cutting off the rotational driving force from the second drive shaft to the second output shaft, and the electric motor applied to the first output shaft
- the rotational driving force is used for a shift operation for driving the shift forks (3 to 6), and the rotational driving force of the electric motor applied to the second output shaft is the shift target. This is used for the select operation for selecting the forks (3 to 6).
- the driving shaft is connected to the tip of the rotating shaft so as to be integrally rotatable, and the rotational driving force is transmitted between the driving shaft and the first output shaft.
- the first electromagnetic clutch for interrupting / interrupting is interposed, and the second electromagnetic clutch for transmitting / interrupting the rotational driving force is interposed between the first output shaft and the second output shaft.
- Conceivable in this case, a complicated transmission mechanism is required, and the structure including the drive shaft, the first and second output shafts, and the first and second electromagnetic clutches may be complicated.
- the rotating shaft extends through the motor housing.
- the first output shaft is disposed on the opposite side of the first drive shaft from the electric motor side, and the first drive shaft and the first output shaft are connected via the first electromagnetic clutch.
- a second output shaft is disposed on the opposite side of the electric motor side with respect to the second drive shaft, and the second drive shaft and the second output shaft are connected via a second electromagnetic clutch. Therefore, the configuration of the transmission can be simplified.
- the selection operation is performed by movement in the axial direction
- the shift operation is performed by rotation around the axis
- the shift selection shaft extends in a direction orthogonal to the rotation axis ( 11)
- a first conversion mechanism (24) for converting the rotational driving force applied to the first output shaft into a force for rotating the shift select shaft about its axis
- the second output shaft And a second conversion mechanism (25) for converting the applied rotational driving force into a force for moving the shift select shaft in the axial direction.
- the rotational driving force applied from the electric motor to the first output shaft is converted into the rotational driving force of the shift select shaft via the first conversion mechanism. Therefore, the rotational driving force applied from the electric motor to the second output shaft is converted into a moving force in the axial direction of the shift select shaft via the second conversion mechanism. That is, the shift select shaft is rotationally driven in the operating state of the first electromagnetic clutch, and the shift select shaft moves in the axial direction in the operating state of the second electromagnetic clutch. Thereby, the rotational drive of the shift select shaft and the axial movement of the shift select shaft can be performed using the driving force of one electric motor.
- a ball screw mechanism (58) having a screw shaft (61) to which a rotational driving force from the first output shaft is applied, and a nut (59) attached to the screw shaft; A first end portion (72) and a second end portion (74); the first end portion is connected to the nut; the second end portion is connected to the shift select shaft; A connecting rod (60) that is coupled so as not to be relatively rotatable and that can swing around the shift select shaft may be included.
- the first conversion mechanism meshes with the worm shaft to which the rotational driving force from the first output shaft is applied and the worm shaft, and the worm gear that applies the rotational driving force of the worm shaft to the shift select shaft. And may be included.
- the second conversion mechanism transmits a rotational driving force from the second output shaft to the pinion (36) provided rotatably around a predetermined rotational axis parallel to the second output shaft. It may include a transmission mechanism (56, 81, 251 and 95) and a rack tooth (35) which is formed on the peripheral surface of the shift select shaft and meshes with the pinion.
- the second conversion mechanism includes a first gear (56) that rotates in response to a rotational driving force from the second output shaft, a transmission shaft (95) that extends parallel to the second output shaft, and the transmission Formed on the peripheral surface of the shift select shaft, a second gear (251) meshed with the first gear, a pinion (36) provided so as to rotate integrally with the transmission shaft. And rack teeth (35) meshing with the pinion, and at least one of the first and second gears may be a sector gear.
- shift select shaft self-weight rotational force acts on the transmission shaft.
- the shift select does not descend (moves in the axial direction) due to its own weight.
- a brake mechanism or the like is not provided in relation to the second output shaft, the rotation shaft rotates by receiving the self-rotation force of the shift select shaft when the rotation shaft and the second output shaft are released. Therefore, there is a risk of allowing the shift select shaft to descend.
- the shift select axis is lowered, the axial position (select position) of the shift select axis may change without being controlled by the control unit.
- the shift select shaft cannot be set to extend in the vertical direction. For this reason, there is a restriction on the mounting state (mounting state) of the apparatus on a vehicle or the like. Therefore, when at least one of the first and second gears is a sector gear, the sector gear may be fan-shaped or semicircular.
- the transmission shaft extends in a direction orthogonal to the shift select shaft, when the shift select shaft extends in the vertical direction, the transmission shaft extends in the left-right direction (horizontal direction or a direction close to horizontal).
- the second gear has a fan shape or a semicircular shape. Therefore, depending on the mounting posture of the second gear to the transmission shaft, the position of the center of gravity of the second gear after mounting is shifted in the radial direction from the rotation axis of the transmission shaft, and the rotational force due to the weight of the second gear (hereinafter referred to as “second gear”).
- the gear self-weight rotating force ”) acts on the transmission shaft.
- the shift selection shaft extending the second gear self-weight rotational force along the vertical direction. If the direction and size are set so as to cancel the shift select shaft's own weight rotational force, the shift select shaft's own weight rotational force is canceled and the transmission shaft does not rotate. Thereby, it is possible to prevent the shift select shaft from being lowered when the rotary shaft and the second output shaft are released. Accordingly, the shift select shaft can be prevented from lowering without employing an electromagnetic clutch or the like provided with a brake mechanism, thereby preventing an increase in cost.
- the second gear may be a sector gear, or may be another type of gear (for example, a spur gear). Since the second output shaft extends in a direction orthogonal to the shift select shaft, when the shift select shaft extends in the vertical direction, the second output shaft extends in the left-right direction (horizontal direction or a direction close to horizontal). It extends.
- the first gear has a fan shape or a semicircular shape.
- first gear the position of the center of gravity of the first gear after mounting shifts in the radial direction from the rotation axis of the transmission shaft, and the rotational force due to the weight of the first gear (hereinafter referred to as “first gear”). 1 gear self-weight rotational force ”) is generated. Then, the first gear self-weight rotation force acts on the transmission shaft that supports the second gear meshing with the first gear so as to be integrally rotatable. At this time, by selecting the number of teeth and / or the weight of the first gear or / and adjusting the mounting posture of the first gear to the transmission shaft, the shift selection shaft extending the first gear self-weight rotational force along the vertical direction.
- the shift select shaft self-weight rotation force is canceled and the transmission shaft does not rotate. Thereby, it is possible to prevent the shift select shaft from being lowered when the rotary shaft and the second output shaft are released. Accordingly, the shift select shaft can be prevented from lowering without employing an electromagnetic clutch or the like provided with a brake mechanism, thereby preventing an increase in cost.
- the transmission according to the embodiment of the present invention includes a select shaft (103) that extends in a direction orthogonal to the rotation shaft and performs the selection operation by rotating around the shaft, and both the rotation shaft and the select shaft.
- the shift shaft (102) that extends in a direction orthogonal to the shaft and performs the shift operation by rotating around the axis, and the rotational driving force applied to the first output shaft, rotate the shift shaft about the axis.
- Conversion mechanism (156; 204).
- the rotational driving force applied from the electric motor to the first output shaft is converted into the rotational driving force of the shift shaft via the third conversion mechanism. Therefore, the rotational driving force applied from the electric motor to the second output shaft is converted into a moving force in the axial direction of the select shaft via the fourth conversion mechanism. That is, the shift shaft is rotationally driven in the operating state of the first electromagnetic clutch, and the select shaft is rotationally driven in the operating state of the second electromagnetic clutch. Thereby, the rotational drive of the shift shaft and the rotational drive of the select shaft can be performed using the driving force of one electric motor.
- the third conversion mechanism includes a screw shaft (first screw shaft) (145) to which a rotational driving force is applied from the first output shaft, and a nut (first nut) attached to the screw shaft ( 143) having a ball screw mechanism (first ball screw mechanism) (142), a first end (144A) and a second end (144B), and the first end is coupled to the nut.
- the second end portion is connected to the shift shaft so as not to rotate relative to the shift shaft, and is a connecting rod (first connecting rod) (144) that can swing around the rotation axis of the shift shaft. May be included.
- the fourth conversion mechanism includes a second ball screw mechanism having a second screw shaft to which a rotational driving force from the second output shaft is applied, and a second nut attached to the second screw shaft; The one end portion is connected to the second nut, and the other end portion is connected to the select connecting shaft connected to the select shaft so as not to be rotatable relative to the select shaft, and around the rotation axis of the select shaft. And a second connecting rod that can swing.
- the third conversion mechanism meshes with the first worm shaft (205) to which the rotational driving force from the first output shaft is applied, and the first worm shaft, and the rotational driving force of the first worm shaft is obtained.
- a first worm gear (206) applied to the shift shaft, and the fourth conversion mechanism includes a second worm shaft (207) to which a rotational driving force is applied from the second output shaft, and the second A second worm gear (208) that meshes with the worm shaft and applies the rotational driving force of the second worm shaft to the select shaft may be included.
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Abstract
Description
この変速装置では、マニュアルトランスミッション(M/T)の変速装置と同様、メインシャフトの複数の変速ギヤとカウンタシャフトの複数の変速ギヤとが全て常時噛み合ったまま回転する。カウンタシャフトの各変速ギヤは、空転状態でカウンタシャフトに取り付けられている。各変速ギヤに一対一に対応付けられたスリーブが、所望の変速ギヤに挿入されることにより、当該変速ギヤとカウンタシャフトとが一体回転可能に連結される。各スリーブは、複数設けられたシフトフォークのいずれかと係合されており、このシフトフォークの駆動によって、対応するスリーブの挿入/非挿入が切り換えられる。また、複数のシフトフォークから、駆動の対象となる前記シフトフォークを選択するセレクト機構が設けられている。
また、特許文献2には、電動駆動部材として、電動アクチュエータに代えて電動モータを採用するものが開示されている。この構成では、第1電動モータの回転駆動力によってシフト動作が行われ、また、第2電動モータの回転駆動力によってセレクト動作が行われる。
そこで、本発明の目的の1つは、1つの電動モータの駆動力を用いてシフト動作およびセレクト動作を行うことができる変速装置を提供することである。
変速装置1は、乗用車やトラックなどの車両に搭載されるものであり、ギヤボックス2を備えている。ギヤボックス2内には、エンジン等からの入力回転を、クラッチ(図示しない。)を介して受け取る入力軸としてのメインシャフト(図示しない。)と、メインシャフトと平行に延びて、プロペラシャフト等に出力回転を伝達する出力軸としてのカウンタシャフト(図示しない。)とが備えられている。各シャフトの途中部には、複数の変速ギヤ(図示しない。)が設けられている。この変速装置1では常時噛み合い式(コンスタントメッシュ方式)が採用されており、メインシャフトの変速ギヤとカウンタシャフトの変速ギヤとは、全て常時噛み合ったまま回転する。カウンタシャフトには変速ギヤが空転状態で取り付けられている。
フォーク軸7~10の周囲(図2に示す上方。)には、シフトセレクト軸11がフォーク軸7~10に直交する方向に延びている。シフトセレクト軸11はその軸線まわりに回転可能に、かつその軸長方向に移動させることができるようになっている。このシフトセレクト軸11の途中部にはシフトレバー12が固定されている。シフトレバー12は、各フォーク軸7~10に選択的に係合可能であり、シフトセレクト軸11の回転によりシフトレバー12をフォーク軸7~10に係合させることができる。具体的には、シフトレバー12は、シフトセレクト軸11に固定されたボス部13と、このボス部13の下端に突設された突出部14とを備える。各フォーク軸7~10には、突出部14を挟持可能な挟持部17,18,19,20がシフトセレクト軸11の長手方向に並んで突設されている。そして、突出部14が挟持部17~20に挟持されることにより、シフトレバー12とフォーク軸7~10との係合が達成される。
ギヤボックス2の周面(外面)には、ギヤボックス2内におけるシフト動作およびセレクト動作を駆動するためのシフト/セレクト駆動装置21が取り付けられている。シフトセレクト軸11の一端側(図1に示す下側。図2に示す右端側。)部分は、ギヤボックス2外に突出して、シフト/セレクト駆動装置21のハウジング22内に進入している。
シフト/セレクト駆動装置21は、電動モータ23と、電動モータ23の回転駆動力を増幅して、シフトセレクト軸11をその中心軸線C1まわりに回転させる力に変換するための第1変換機構24と、電動モータ23の回転駆動力を増幅して、シフトセレクト軸11をその軸長方向(図3に示す左右方向。)に移動させる力に変換するための第2変換機構25と、電動モータ23の回転駆動力の伝達先を、第1変換機構24と第2変換機構25との間で切換える切換えユニット26とを備えている。つまり、このシフト/セレクト駆動装置21は、電動アクチュエータユニットを構成しており、この実施形態に示すような変速装置1に適用されることにより、シフト/セレクト駆動装置として機能する。
電動モータ23のロータに同軸的に固定された回転軸40が、シフトセレクト軸11と直交する一方向(図3に示す左右方向。)に沿って延び、その先端部がモータハウジング38外に突出している(図3に示すC2は、回転軸40の回転軸線。)。
なお、第1電磁クラッチ43および第2電磁クラッチ45を備えた電磁クラッチ機構には、ブレーキ機構が備えられている。具体的には、第2電磁クラッチ45が非稼動状態にある状態、すなわち回転軸40と第2出力軸44とが解放された状態でも、第2出力軸44は電磁クラッチ機構により固定保持されている。
そして、切換えユニット26をハウジング22内に装着する際は、切換えユニット26をハウジング22の開口部を通して収容部30内に進入させると、切換えユニット26の一方端が段部31と係合して、所定の収容位置に装着される。これにより、切換えユニット26のハウジング22内への装着を、簡単に行うことができる。
接続ロッド60は、その第1端部72(図3および図4における上端部。)に設けられ、ナット59に連結するための第1連結部73と、接続ロッド60の第2端部74(図3および図4における下端部。)に設けられ、シフトセレクト軸11に連結するための第2連結部75(図4参照。)とを備えている。
さらに、ボールねじ機構58を用いて、第1出力軸42の回転駆動力が直線方向運動に変換されるので、シフト/セレクト駆動装置21の小型化をより一層図ることができる。
この第2実施形態にかかる変速装置101では、シフト動作/セレクト動作を行うためのシフトセレクト軸11(図2~図4参照。)に代えて、シフト動作を行うためのシフト軸102およびセレクト動作を行うためのセレクト軸103が、ギヤボックス2(図1参照。)内に設けられている。シフト軸102およびセレクト軸103は互いに直交する方向に延びている。シフト軸102の軸まわりの回転により、シフトフォーク3~6(図2参照。)を駆動するためのシフト動作が行われ、また、セレクト軸103の軸方向への移動により、駆動の対象となるシフトフォーク3~6を選択するためのセレクト動作が行われる。シフト軸102の一端側部分(図5に示す下側部分。)はギヤボックス2外に突出して、次に述べるシフト/セレクト駆動装置104のハウジングの周辺領域にまで達している。また、セレクト軸103の一端側部分(図5に示す紙面手前側の部分。)は、ギヤボックス2外に突出している。
まず、電動モータ109について説明する。電動モータ109として、ブラシレスモータが採用されている。電動モータ109は、モータハウジング111と、このモータハウジング111内に収容されたロータ112およびステータ113とを備えている。ロータ112は円環状であり、その外周部には、複数の永久磁石が保持されている。ロータ112の外周は、N極およびS極が交互に入れ替わる磁極となっている。ロータ112には、回転軸114が同軸的に固定されている。ロータ112と回転軸114とは同行回転可能である(図6Aおよび図6BにおけるC2は、回転軸114の回転軸線)。
円筒ブラケット115は、ボルト125によって第1カバーブラケット116に固定されており、ボルト126によって第2カバーブラケット118に固定されている。
第1接続ロッド144の第1端部144A(図6Aにおける上端部。)には、第1ナット143に連結するための第1連結部152が設けられている。また、第1接続ロッド144の第2端部144B(図3および図4における下端部。)は、シフト軸102に固定されている(相対回転不能に設けられている)。
したがって、第1および第2電磁クラッチ130,159を選択的に稼動させることにより、シフト動作およびセレクト動作を個別に行うことができる。これにより、1つの電動モータ109の駆動力を用いてシフト動作およびセレクト動作を行うことができる。
なお、図6Aおよび図6Bには図示していないが、シフト軸102および/またはセレクト軸103には、その軸102,103の回転量を検出するための回転量センサが設けられていてもよい。この回転量センサは、たとえば第1ナット143(第2ナット172)の軸方向の移動量を検出し、これに基づいて、シフト軸102やセレクト軸103の回転量を検出するものであってもよい。
ギヤボックス2の周面(外面)には、ギヤボックス2内におけるシフト動作およびセレクト動作を駆動するためのシフト/セレクト駆動装置202が取り付けられている。シフト軸102には、シフト/セレクト駆動装置202の第1ウォーム歯車206が固定連結されている。また、セレクト軸103には、シフト/セレクト駆動装置202の第2ウォーム歯車208が固定連結されている。
この第3実施形態にかかる変速装置201のシフト/セレクト駆動装置202が、第2実施形態にかかるシフト/セレクト駆動装置104と相違する点は、ボールねじ機構142,170および接続ロッド144を備えた第3変換機構131ならびに第4変換機構156に代えて、ウォーム軸205,207と、このウォーム軸205,207と噛み合うウォーム歯車206,208とを備えた第3変換機構203および第4変換機構204を設けた点である。
したがって、第1および第2電磁クラッチ130,159を選択的に稼動させることにより、シフト動作およびセレクト動作を個別に行うことができる。これにより、1つの電動モータ109の駆動力を用いてシフト動作およびセレクト動作を行うことができる。
第2電磁クラッチ45が稼動状態にある場合、すなわち回転軸40と第2出力軸44とが連結されている場合は、シフトセレクト軸11がその自重により下降する(軸方向に移動する)ことはない。しかしながら、この実施形態では、第2出力軸44にブレーキ機構などが設けられていない。そのため、第2電磁クラッチ45が非稼動状態にある場合、すなわち回転軸40と第2出力軸44とが解放されていると、回転軸40は、シフトセレクト軸自重回転力を受けて回転し、そのため、シフトセレクト軸11の下降を許容するおそれがある。シフトセレクト軸11が回転すると、ECU88の制御によらずにシフトセレクト軸11の軸方向位置(セレクト位置)が変化するおそれがある。
また、図9のように、第2歯車251の曲線部分(円弧)が側方(第1歯車56側)を向くような姿勢で、第2歯車251が伝達軸95に取り付けられていると、第2歯車251の重心位置が伝達軸95の回転軸線から径方向にずれ、第2歯車251の自重による回転力(以下、「第2歯車自重回転力」という。図9にて実線で図示)が伝達軸95に作用する。
なお、この第4実施形態では、第2歯車(セクタ歯車)251が半円状をなしている場合を例に挙げて説明したが、扇形状をなすセクタ歯車を第2歯車として用いることもできる。
たとえば、第4実施形態において、第1歯車にセクタ歯車を採用することができる。この場合、第2歯車は平歯車からなっていてもよいし、セクタ歯車からなっていてもよい。セクタ歯車からなる第1歯車が第2出力軸44に取り付けられていると、第1歯車1の重心位置が第2出力軸44の回転軸線から径方向にずれ、第1歯車の自重による回転力(以下、「第1歯車自重回転力」という)が第2出力軸44に生じ、この第1歯車自重回転力が伝達軸95に作用する。そして、この第1歯車自重回転力を、シフトセレクト軸自重回転力を打ち消すような向きおよび大きさに設定すれば、シフトセレクト軸自重回転力は打ち消されて、伝達軸95は回転しない。これにより、回転軸40と第2出力軸44とが解放されている場合におけるシフトセレクト軸11の下降を確実に防止することができる。
また、第2実施形態において、セレクト軸103と第2減速機ユニット108とを直接連結する場合は、第1端部が第2ナット172に連結されるとともに、第2端部がセレクト軸に固定され(相対回転不能に連結され)た第2接続ロッドを設けることができる。この場合、第2接続ロッドの第1端部には、第2ナット172に連結するための連結部が設けられている。この連結部は、第2実施形態に示す連結部181と同様の構成であり、第2ナット172に係合する。
その他、特許請求の範囲に記載された事項の範囲で種々の設計変更を施すことが可能である。
しかしながら、この場合、複雑な伝達機構が必要になり、駆動軸、第1および第2出力軸、ならびに第1および第2電磁クラッチを含む構造が複雑化するおそれがあるばかりか、第1および第2電磁クラッチが回転軸の軸方向に沿って延びるようになるので、装置が大型化する場合がある。
また、前記駆動軸は、軸体(46)と、前記軸体から径方向外方に向けて張り出した駆動ハブ(47)とを備えており、前記第1および第2出力軸は、前記駆動ハブを挟んで配置されていることが好ましい。この場合、装置の小型化を図りつつ、駆動軸から第1および第2出力軸へのトルク伝達の伝達効率を大きく保つことができる。
本発明の実施形態に係る変速装置(101;201)は、モータハウジング(111)と、当該モータハウジングを貫通して延びる回転軸(114)とを有する電動モータ(109)と、前記回転軸の一端側に当該回転軸と一体回転可能に連結される第1駆動軸(120)と、前記第1駆動軸に対して前記電動モータと反対側に、当該第1駆動軸と同軸に回転可能に設けられた第1出力軸(129)と、前記第1駆動軸からの回転駆動力を前記第1出力軸に伝達/遮断する第1電磁クラッチ(130)と、前記回転軸における前記一端と反対側の他端側に、当該回転軸と回転軸と一体回転可能に連結される第2駆動軸(123)と、前記第2駆動軸に対して前記電動モータと反対側に、当該第2駆動軸と同軸に回転可能に設けられた第2出力軸(158)と、前記第2駆動軸からの回転駆動力を前記第2出力軸に伝達/遮断する第2電磁クラッチ(159)とを含み、前記第1出力軸に付与される前記電動モータの回転駆動力が、シフトフォーク(3~6)を駆動するためのシフト動作に用いられており、前記第2出力軸に付与される前記電動モータの回転駆動力が、駆動の対象となる前記シフトフォーク(3~6)を選択するためのセレクト動作に用いられている。
しかしながら、この場合、複雑な伝達機構が必要になり、駆動軸、第1および第2出力軸、ならびに第1および第2電磁クラッチを含む構造が複雑化する場合がある。
前記第2変換機構が、前記第2出力軸と平行な所定の回転軸線まわりに回転可能に設けられたピニオン(36)と、前記ピニオンに、前記第2出力軸からの回転駆動力を伝達する伝達機構(56,81,251,95)と、前記シフトセレクト軸の周面に形成され、前記ピニオンと噛み合うラック歯(35)とを含んでいてもよい。
そこで、第1および第2歯車の少なくとも一方がセクタ歯車からなっている場合には、セクタ歯車は扇形状または半円状をなしているとよい。
本発明の実施形態に係る変速装置は、前記回転軸と直交する方向に延びて、軸まわりへの回転により前記セレクト動作が行われるセレクト軸(103)と、前記回転軸および前記セレクト軸の双方に直交する方向に延びて、軸まわりへの回転により前記シフト動作が行われるシフト軸(102)と、前記第1出力軸に付与された回転駆動力を、前記シフト軸をその軸線まわりに回転させる力に変換するための第3変換機構(131;203)と、前記第2出力軸に付与された回転駆動力を、前記セレクト軸をその軸線まわりに回転させる力に変換するための第4変換機構(156;204)とを含む。
23…電動モータ、24…第1変換機構、25…第2変換機構、
35…ラック歯、36…ピニオン、40…回転軸、41…駆動軸、
42…第1出力軸、43…第1電磁クラッチ、44…第2出力軸、
45…第2電磁クラッチ、46…軸体、56…第1歯車(伝達機構)、
58…ボールねじ機構、59…ナット、60…接続ロッド、61…ねじ軸、
72…第1端部、74…第2端部、81…第2歯車(伝達機構)、
95…伝達軸(伝達機構)、102…シフト軸、103…セレクト軸、
109…電動モータ、111…モータハウジング、114…回転軸、
120…第1駆動軸、123…第2駆動軸、129…第1出力軸、
130…第1電磁クラッチ、131,203…第3変換機構、
142…第1ボールねじ機構(ボールねじ機構)、
143…第1ナット(ナット)、144…第1接続ロッド(接続ロッド)、
144A…第1端部、144B…第2端部、
145…第1ねじ軸(ねじ軸)、156,204…第4変換機構、
158…第2出力軸、159…第2電磁クラッチ、
205…第1ウォーム軸、206…第1ウォーム歯車、
207…第2ウォーム軸、208…第2ウォーム歯車、
251…第2歯車(伝達機構)
Claims (9)
- 回転軸を有する電動モータと、
前記電動モータの回転軸と同軸に回転可能に設けられた第1出力軸と、
前記回転軸からの回転駆動力を前記第1出力軸に伝達/遮断する第1電磁クラッチと、
前記回転軸と同軸に回転可能に設けられた第2出力軸と、
前記回転軸からの回転駆動力を前記第2出力軸に伝達/遮断する第2電磁クラッチとを含み、
前記第1出力軸に付与される前記電動モータの回転駆動力が、シフトフォークを駆動するためのシフト動作に用いられ、
前記第2出力軸に付与される前記電動モータの回転駆動力が、駆動の対象となる前記シフトフォークを選択するためのセレクト動作に用いられる、変速装置。 - 回転軸を有する電動モータと、
前記電動モータの回転軸と同軸に設けられ、前記電動モータの回転駆動力によって回転駆動される駆動軸と、
前記駆動軸の先端側に、当該駆動軸と同軸に回転可能に設けられた第1出力軸と、
前記駆動軸からの回転駆動力を前記第1出力軸に伝達/遮断する第1電磁クラッチと、
前記駆動軸と同軸に回転可能に設けられた第2出力軸と、
前記駆動軸からの回転駆動力を前記第2出力軸に伝達/遮断する第2電磁クラッチとを含み、
前記第2出力軸が、円環状をなして前記駆動軸の周囲を取り囲み、
前記第1出力軸が、前記駆動軸および前記第2出力軸に対して、前記電動モータとは反対側に配置され、
前記第1出力軸に付与される前記電動モータの回転駆動力が、シフトフォークを駆動するためのシフト動作、および駆動の対象となる前記シフトフォークを選択するためのセレクト動作の一方に用いられており、
前記第2出力軸に付与される前記電動モータの回転駆動力が、前記シフト動作および前記セレクト動作の他方に用いられている、変速装置。 - 前記駆動軸は、軸体と、前記軸体から径方向外方に向けて張り出した駆動ハブとを備えており、
前記第1および第2出力軸は、前記駆動ハブを挟んで配置されている、請求項2記載の変速装置。 - 前記電動モータ、前記駆動軸、前記第1出力軸、前記第2出力軸、前記第1電磁クラッチ、および前記第2電磁クラッチがユニット化されている、請求項2記載の変速装置。
- 軸方向への移動により前記セレクト動作が行われるとともに、軸まわりへの回転により前記シフト動作が行われ、前記回転軸と直交する方向に延びるシフトセレクト軸と、
前記第1出力軸に付与された回転駆動力を、前記シフトセレクト軸をその軸線まわりに回転させる力に変換するための第1変換機構と、
前記第2出力軸に付与された回転駆動力を、前記シフトセレクト軸を軸方向に移動させる力に変換するための第2変換機構とを含む、請求項1記載の変速装置。 - 前記第1変換機構が、
前記第1出力軸からの回転駆動力が付与されるねじ軸と、前記ねじ軸に取り付けられたナットとを有するボールねじ機構と、
第1端部および第2端部を有し、前記第1端部が前記ナットに連結されるとともに、前記第2端部が前記シフトセレクト軸に、当該シフトセレクト軸に対する相対回転不能に連結されており、前記シフトセレクト軸の回転軸線まわりに揺動可能な接続ロッドとを含む、請求項5記載の変速装置。 - 前記第2変換機構が、
前記第2出力軸と平行な所定の回転軸線まわりに回転可能に設けられたピニオンと、
前記ピニオンに、前記第2出力軸からの回転駆動力を伝達する伝達機構と、
前記シフトセレクト軸の周面に形成され、前記ピニオンと噛み合うラック歯とを含む、
請求項5記載の変速装置。 - 前記第2変換機構が、
前記第2出力軸からの回転駆動力を受けて回転する第1歯車と、
前記第2出力軸と平行と延びる伝達軸と、
前記伝達軸に一体回転可能に設けられ、前記第1歯車と噛合う第2歯車と、
前記伝達軸に一体回転可能に設けられたピニオンと、
前記シフトセレクト軸の周面に形成され、前記ピニオンと噛み合うラック歯とを含み、
前記第1および第2歯車の少なくとも一方がセクタ歯車からなる、請求項5記載の変速装置。 - モータハウジングと、当該モータハウジングを貫通して延びる回転軸とを有する電動モータと、
前記回転軸の一端側に当該回転軸と一体回転可能に連結される第1駆動軸と、
前記第1駆動軸に対して前記電動モータと反対側に、当該第1駆動軸と同軸に回転可能に設けられた第1出力軸と、
前記第1駆動軸からの回転駆動力を前記第1出力軸に伝達/遮断する第1電磁クラッチと、
前記回転軸における前記一端と反対側の他端側に、当該回転軸と回転軸と一体回転可能に連結される第2駆動軸と、
前記第2駆動軸に対して前記電動モータと反対側に、当該第2駆動軸と同軸に回転可能に設けられた第2出力軸と、
前記第2駆動軸からの回転駆動力を前記第2出力軸に伝達/遮断する第2電磁クラッチとを含み、
前記第1出力軸に付与される前記電動モータの回転駆動力が、シフトフォークを駆動するためのシフト動作に用いられており、
前記第2出力軸に付与される前記電動モータの回転駆動力が、駆動の対象となる前記シフトフォークを選択するためのセレクト動作に用いられている、変速装置。
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Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN103851181A (zh) * | 2012-12-06 | 2014-06-11 | 爱信Ai株式会社 | 自动变速器的换档操作装置 |
Families Citing this family (25)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102008000638B4 (de) * | 2008-03-13 | 2022-05-25 | Zf Friedrichshafen Ag | Betätigungseinrichtung zum Betätigen zumindest einer Schalteinrichtung und Verfahren zum Montieren und Demontieren derselben |
JP5472729B2 (ja) | 2010-02-24 | 2014-04-16 | 株式会社ジェイテクト | 変速装置 |
JP5440861B2 (ja) | 2010-03-24 | 2014-03-12 | 株式会社ジェイテクト | 変速機駆動装置 |
JP2013007394A (ja) * | 2011-06-22 | 2013-01-10 | Jtekt Corp | 変速駆動装置 |
JP2013096544A (ja) | 2011-11-04 | 2013-05-20 | Jtekt Corp | 変速駆動装置 |
JP2013100857A (ja) | 2011-11-08 | 2013-05-23 | Jtekt Corp | 変速駆動装置 |
JP2013100858A (ja) | 2011-11-08 | 2013-05-23 | Jtekt Corp | 電動アクチュエータ |
JP2013100856A (ja) | 2011-11-08 | 2013-05-23 | Jtekt Corp | 変速駆動装置 |
JP2013104500A (ja) | 2011-11-15 | 2013-05-30 | Jtekt Corp | 電動アクチュエータ |
CN102619969B (zh) * | 2012-04-16 | 2014-10-01 | 吉林大学 | 电控电动六挡自动换挡*** |
JP2014054160A (ja) * | 2012-08-08 | 2014-03-20 | Jtekt Corp | 電動アクチュエータ |
CN103016701A (zh) * | 2012-12-04 | 2013-04-03 | 中国北方车辆研究所 | 机械式自动变速***选换档执行机构 |
DE102013207871A1 (de) * | 2013-04-30 | 2014-10-30 | Schaeffler Technologies Gmbh & Co. Kg | Getriebeaktor für ein Kraftfahrzeuggetriebe sowie Steuerung zur Ansteuerung eines Getriebeaktors |
WO2015060209A1 (ja) * | 2013-10-24 | 2015-04-30 | トヨタ自動車株式会社 | 無段変速機の変速制御装置 |
DE102014202279A1 (de) * | 2014-02-07 | 2015-08-13 | Bühler Motor GmbH | Elektromotorischer Antrieb |
CN106133407B (zh) * | 2014-03-26 | 2018-10-02 | 舍弗勒技术股份两合公司 | 单马达变速器执行器及其控制方法 |
JP6224517B2 (ja) * | 2014-05-09 | 2017-11-01 | 京浜精密工業株式会社 | 変速操作機構 |
US9976646B2 (en) * | 2015-05-28 | 2018-05-22 | Automotive Research & Testing Center | Angle regulation device |
WO2019061417A1 (zh) * | 2017-09-30 | 2019-04-04 | 深圳市艾莱茵科技有限公司 | 电磁离合器及变速箱 |
JP2019122081A (ja) * | 2017-12-28 | 2019-07-22 | 日本電産トーソク株式会社 | 電動アクチュエータ |
JP6985423B2 (ja) * | 2018-01-16 | 2021-12-22 | 津田工業株式会社 | シフト装置 |
CN109973648A (zh) * | 2019-03-19 | 2019-07-05 | 西安法士特汽车传动有限公司 | 一种变速箱选档降阻机构及其选档方法 |
WO2021027556A1 (zh) * | 2019-08-09 | 2021-02-18 | 济南豪特创新管理咨询合伙企业(有限合伙) | 回转件组合装置及其连接轴 |
CN111229581A (zh) * | 2019-08-09 | 2020-06-05 | 济南豪特创新管理咨询合伙企业(有限合伙) | 回转件组合装置 |
CN111911620B (zh) * | 2020-07-29 | 2021-11-12 | 中国航发湖南动力机械研究所 | 多功能推杆操纵装置 |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0312623U (ja) * | 1989-06-22 | 1991-02-08 | ||
JPH09112688A (ja) * | 1995-07-29 | 1997-05-02 | Ford Motor Co | 電気式ギヤシフト機構 |
JPH10148256A (ja) * | 1996-11-19 | 1998-06-02 | Aichi Mach Ind Co Ltd | 歯車式変速機の自動変速装置 |
JP2000035127A (ja) * | 1998-07-17 | 2000-02-02 | Aisin Seiki Co Ltd | 同期かみあい式歯車変速機における電動式セレクト・シフト装置 |
JP2002139146A (ja) | 2000-11-02 | 2002-05-17 | Aisin Ai Co Ltd | 同期噛合式変速機における変速制御装置 |
JP2003314687A (ja) | 2002-04-25 | 2003-11-06 | Hino Motors Ltd | 変速装置 |
WO2005057051A1 (ja) * | 2003-12-11 | 2005-06-23 | Hitachi, Ltd. | 電動アクチュエータとその制御装置 |
Family Cites Families (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2770193B2 (ja) * | 1989-09-27 | 1998-06-25 | 株式会社ニコン | 同軸ハンドル部材の粗微動式駆動装置 |
JPH07308837A (ja) * | 1994-05-12 | 1995-11-28 | Teijin Seiki Co Ltd | 電動推力発生装置 |
US6230577B1 (en) * | 1999-01-20 | 2001-05-15 | Borgwarner Inc. | Electric shift control assembly |
FR2789743A1 (fr) * | 1999-02-17 | 2000-08-18 | Mannesmann Sachs Ag | Boite de vitesses automatique |
JP4516652B2 (ja) * | 2000-01-27 | 2010-08-04 | アイシン・エーアイ株式会社 | 歯車式自動変速装置におけるセレクトゲート位置設定装置及び方法 |
US6694834B2 (en) * | 2002-03-22 | 2004-02-24 | New Venture Gear, Inc. | Control system for transfer case range shift |
JP4447226B2 (ja) * | 2003-02-20 | 2010-04-07 | アイシン・エーアイ株式会社 | 車両変速機のセレクト制御装置 |
EP1538370A3 (en) * | 2003-12-05 | 2011-11-30 | Honda Motor Co., Ltd. | Transmission control system |
JP3958740B2 (ja) * | 2003-12-17 | 2007-08-15 | 本田技研工業株式会社 | 変速機の制御装置 |
DE102005001525A1 (de) * | 2005-01-13 | 2006-07-27 | Zf Friedrichshafen Ag | Fahrzeuggetriebe mit integriertem Elektromotor |
US20100107811A1 (en) * | 2007-03-15 | 2010-05-06 | Mccloy Chad | Range and Mode Shift System for Two-Speed On-Demand Transfer Case |
CN101387332B (zh) * | 2007-09-14 | 2012-11-21 | 比亚迪股份有限公司 | 一种多功率流传动*** |
-
2010
- 2010-03-24 JP JP2010068017A patent/JP5440862B2/ja not_active Expired - Fee Related
- 2010-08-31 US US13/390,235 patent/US8714041B2/en not_active Expired - Fee Related
- 2010-08-31 MY MYPI2012000767A patent/MY158644A/en unknown
- 2010-08-31 EP EP10813693.8A patent/EP2474760B1/en not_active Not-in-force
- 2010-08-31 CN CN201080038651XA patent/CN102483155A/zh active Pending
- 2010-08-31 EP EP12196312.8A patent/EP2570702B1/en not_active Not-in-force
- 2010-08-31 WO PCT/JP2010/064796 patent/WO2011027744A1/ja active Application Filing
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0312623U (ja) * | 1989-06-22 | 1991-02-08 | ||
JPH09112688A (ja) * | 1995-07-29 | 1997-05-02 | Ford Motor Co | 電気式ギヤシフト機構 |
JPH10148256A (ja) * | 1996-11-19 | 1998-06-02 | Aichi Mach Ind Co Ltd | 歯車式変速機の自動変速装置 |
JP2000035127A (ja) * | 1998-07-17 | 2000-02-02 | Aisin Seiki Co Ltd | 同期かみあい式歯車変速機における電動式セレクト・シフト装置 |
JP2002139146A (ja) | 2000-11-02 | 2002-05-17 | Aisin Ai Co Ltd | 同期噛合式変速機における変速制御装置 |
JP2003314687A (ja) | 2002-04-25 | 2003-11-06 | Hino Motors Ltd | 変速装置 |
WO2005057051A1 (ja) * | 2003-12-11 | 2005-06-23 | Hitachi, Ltd. | 電動アクチュエータとその制御装置 |
Non-Patent Citations (1)
Title |
---|
See also references of EP2474760A4 * |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN103851181A (zh) * | 2012-12-06 | 2014-06-11 | 爱信Ai株式会社 | 自动变速器的换档操作装置 |
Also Published As
Publication number | Publication date |
---|---|
JP5440862B2 (ja) | 2014-03-12 |
CN102483155A (zh) | 2012-05-30 |
JP2011075097A (ja) | 2011-04-14 |
MY158644A (en) | 2016-10-31 |
EP2474760A4 (en) | 2012-07-11 |
US20120144942A1 (en) | 2012-06-14 |
US8714041B2 (en) | 2014-05-06 |
EP2474760B1 (en) | 2013-12-25 |
EP2570702A1 (en) | 2013-03-20 |
EP2474760A1 (en) | 2012-07-11 |
EP2570702B1 (en) | 2014-01-01 |
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