WO2010016161A1 - 鞍乗型車両用の有段式自動変速装置、それを備えるパワーユニット、及びそれを備える鞍乗型車両 - Google Patents
鞍乗型車両用の有段式自動変速装置、それを備えるパワーユニット、及びそれを備える鞍乗型車両 Download PDFInfo
- Publication number
- WO2010016161A1 WO2010016161A1 PCT/JP2009/000139 JP2009000139W WO2010016161A1 WO 2010016161 A1 WO2010016161 A1 WO 2010016161A1 JP 2009000139 W JP2009000139 W JP 2009000139W WO 2010016161 A1 WO2010016161 A1 WO 2010016161A1
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- WO
- WIPO (PCT)
- Prior art keywords
- clutch
- shaft
- automatic transmission
- type vehicle
- stepped automatic
- Prior art date
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Classifications
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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
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
- F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/10—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts with one or more one-way clutches as an essential feature
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62K—CYCLES; CYCLE FRAMES; CYCLE STEERING DEVICES; RIDER-OPERATED TERMINAL CONTROLS SPECIALLY ADAPTED FOR CYCLES; CYCLE AXLE SUSPENSIONS; CYCLE SIDE-CARS, FORECARS, OR THE LIKE
- B62K2202/00—Motorised scooters
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H2057/0203—Gearboxes; Mounting gearing therein the gearbox is associated or combined with a crank case of an engine
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H2057/02039—Gearboxes for particular applications
- F16H2057/02043—Gearboxes for particular applications for vehicle transmissions
- F16H2057/02047—Automatic transmissions
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H2057/02039—Gearboxes for particular applications
- F16H2057/02043—Gearboxes for particular applications for vehicle transmissions
- F16H2057/02065—Gearboxes for particular applications for vehicle transmissions for motorcycles or squads
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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
- Y10T74/19242—Combined gear and clutch
Definitions
- the present invention relates to a stepped automatic transmission for a straddle-type vehicle, a power unit including the same, and a straddle-type vehicle including the same.
- a stepped automatic transmission is known.
- the stepped automatic transmission generally has higher energy transmission efficiency than a belt-type continuously variable transmission (CVT). For this reason, in recent years, the need for a stepped automatic transmission has increased.
- CVT continuously variable transmission
- Patent Document 1 discloses a 3-speed stepped automatic transmission.
- FIG. 14 is a cross-sectional view of the three-speed stepped automatic transmission 200 disclosed in Patent Document 1.
- an automatic centrifugal start clutch 202 using a planetary gear and a drive sprocket 203 are provided on the left side portion of the crankshaft 201.
- the rotation of the crankshaft 201 is transmitted to the drive sprocket 203 via the automatic centrifugal start clutch 202.
- a main shaft 204 is disposed behind the crankshaft 201.
- a driven sprocket 205 is attached to the main shaft 204.
- a chain 206 is wound between the driven sprocket 205 and the drive sprocket 203.
- An automatic centrifugal high speed clutch 207 is disposed on the main shaft 204. In the stepped automatic transmission 200, the automatic centrifugal high speed clutch 207 switches between the second speed and the third speed.
- Patent Document 1 the automatic centrifugal start clutch 202 and the automatic centrifugal high speed clutch 207 are arranged in the front-rear direction. Thereby, a relatively narrow stepped automatic transmission is realized.
- Japanese Utility Model Publication No. 62-23349 Japanese Utility Model Publication No. 62-23349
- the present invention has been made in view of such points, and an object thereof is to concentrate masses in the front-rear direction in a stepped automatic transmission.
- a stepped automatic transmission for a saddle-ride type vehicle includes an input shaft, an intermediate shaft, an output shaft, a first clutch, a first power transmission mechanism, a second clutch, 2 power transmission mechanisms.
- the intermediate shaft is disposed behind the input shaft.
- the first clutch is intermittently engaged according to the rotational speed of the input shaft.
- the first power transmission mechanism transmits the rotation of the input shaft to the intermediate shaft when the first clutch is connected.
- the second clutch is provided on the intermediate shaft.
- the second clutch is intermittently engaged according to the rotational speed of the intermediate shaft.
- the second power transmission mechanism transmits the rotation of the intermediate shaft to the output shaft when the second clutch is connected.
- the front end of the second clutch is positioned in front of the rear end of the first clutch when viewed from the axial direction of the input shaft. Yes.
- the power unit according to the present invention includes the stepped automatic transmission according to the present invention and a power source for rotating the input shaft.
- a straddle-type vehicle according to the present invention includes the power source according to the present invention. (The invention's effect)
- mass concentration in the front-rear direction can be achieved in the stepped automatic transmission.
- FIG. 1 is a left side view of the motorcycle according to the first embodiment.
- FIG. 2 is a cross-sectional view of the engine unit.
- FIG. 3 is a schematic left side view showing the shaft arrangement of the engine unit.
- FIG. 4 is a partial cross-sectional view of the engine unit.
- FIG. 5 is a schematic left side view showing the shaft arrangement of the engine unit.
- FIG. 6 is a schematic diagram showing the configuration of the engine unit.
- FIG. 7 is a partial cross-sectional view of the engine unit showing the configuration of the downstream clutch group.
- FIG. 8 is a conceptual diagram showing an oil circuit.
- FIG. 9 is a schematic diagram for explaining a power transmission path at the first speed in the transmission.
- FIG. 10 is a schematic diagram for explaining a power transmission path at the second speed in the transmission.
- FIG. 9 is a schematic diagram for explaining a power transmission path at the first speed in the transmission.
- FIG. 10 is a schematic diagram for explaining a power transmission path at the second speed in
- FIG. 11 is a schematic diagram for explaining a power transmission path at the third speed in the transmission.
- FIG. 12 is a schematic diagram for explaining the power transmission path at the fourth speed in the transmission.
- FIG. 13 is a schematic diagram illustrating a configuration of an engine unit according to the second embodiment.
- FIG. 14 is a cross-sectional view of the stepped automatic transmission disclosed in Patent Document 1.
- the motorcycle 1 described in the present embodiment is a scooter.
- the saddle riding type vehicle is not limited to the scooter.
- the straddle-type vehicle of the present invention refers to a general vehicle on which a rider rides.
- the saddle riding type vehicle of the present invention includes ATV (All Terrain Vehicle) is also included.
- ATVs are also called off-road vehicles.
- a motorcycle refers to a vehicle that has front wheels and rear wheels and changes the traveling direction by tilting the vehicle body.
- motorcycles include those in which at least one of a front wheel and a rear wheel is constituted by a plurality of wheels.
- motorcycles include motorcycles, mopeds, scooters and off-road vehicles.
- the motorcycle 1 includes a body frame 10.
- the vehicle body frame 10 has a head pipe (not shown).
- the head pipe extends slightly diagonally forward and downward in the front portion of the vehicle.
- a steering shaft (not shown) is rotatably inserted into the head pipe.
- a handle 12 is provided at the upper end of the steering shaft.
- a front fork 15 is connected to the lower end of the steering shaft.
- a front wheel 16 is rotatably attached to the lower end portion of the front fork 15.
- a body cover 13 is attached to the body frame 10. A part of the body frame 10 is covered with the body cover 13. A seat 14 on which a rider sits is attached to the body frame 10.
- a foot step 17 for placing the rider's foot is provided on both sides of the motorcycle 1 in the vehicle width direction.
- a side stand 23 is attached to the body frame 10 at substantially the center of the vehicle.
- the motorcycle 1 is provided with an engine unit 20 as a power unit.
- a rear wheel 18 is attached to the output shaft 33 of the engine unit 20.
- a vehicle speed sensor 88 is disposed with respect to the output shaft 33.
- the vehicle speed sensor 88 detects the vehicle speed.
- the vehicle speed sensor 88 outputs the detected vehicle speed to an ECU (electronic control unit) 138 shown in FIG.
- the engine unit 20 is a unit swing type engine unit.
- the engine unit 20 is suspended from the vehicle body frame 10 so as to be swingable. Specifically, a pivot shaft 25 extending in the vehicle width direction is attached to the body frame 10.
- the engine unit 20 includes a casing 28.
- An engine bracket 21 as a mounting portion is provided on the lower part of the front side of the casing 28.
- the engine bracket 21 is formed with a mounting hole 21a to which the pivot shaft 25 is fixed.
- a pivot shaft 25 is inserted into the mounting hole 21a. Thereby, the engine unit 20 is attached to the body frame 10 so as to be swingable.
- the engine bracket 21 is located in front of the axis C1 of the input shaft 52 of the stepped automatic transmission 31 described later.
- the engine bracket 21 is located below the axis C1 of the input shaft 52.
- the center C0 of the mounting hole 21a is located below the axis C1 of the input shaft 52.
- the “center in the side view of the attachment portion” refers to the center in the side view of the attachment hole.
- a cushion unit 22 is attached between the engine unit 20 and the vehicle body frame 10.
- the cushion unit 22 suppresses the swing of the engine unit 20.
- the engine unit 20 includes an engine 30 as a power source and a stepped automatic transmission 31.
- power source refers to a mechanism for generating power.
- Power source includes an engine and a motor.
- the engine 30 includes a crankcase 32.
- the crankcase 32 constitutes the casing 28 together with a transmission cover 50 described later and a generator cover (not shown).
- a crank chamber 35 is formed inside the crankcase 32.
- a crankshaft 34 extending in the vehicle width direction is accommodated in the crank chamber 35.
- a connecting rod 36 is connected to the crankshaft 34 by a crankpin 29.
- a piston 39 shown in FIG. 6 is attached to the tip of the connecting rod 36.
- a cylinder body 37 is connected to the front side portion of the crankcase 32.
- a cylinder head 42 shown in FIG. 8 is connected to the tip of the cylinder body 37.
- a cylinder 38 in which the piston 39 is accommodated is defined in the cylinder body 37.
- the engine 30 is provided with a kick starter 100 and a cell motor 101.
- the rider of the motorcycle 1 can start the engine 30 by operating the kick starter 100 or driving the cell motor 101.
- the kick starter 100 has a kick pedal 24.
- the kick pedal 24 is disposed on the right side of the transmission cover 50.
- the kick pedal 24 is attached to the kick shaft 102 shown in FIG.
- the kick shaft 102 is supported by the transmission cover 50.
- the axis C ⁇ b> 10 of the kick shaft 102 is disposed behind and above the axis C ⁇ b> 1 of the crankshaft 34.
- a compression coil spring 103 is provided between the kick shaft 102 and the crankcase 32. By this compression coil spring, an urging force in the reverse rotation direction is applied to the kick shaft 102 rotated by the rider's operation.
- a shaft 105 is disposed above the kick shaft 102.
- the shaft 105 is disposed from the transmission cover 50 to the crankcase 32 in the vehicle width direction.
- the shaft center C ⁇ b> 11 of the shaft 105 is disposed substantially above the shaft center C ⁇ b> 10 of the kick shaft 102.
- the axis C11 of the shaft 105 and the axis C10 of the kick shaft 102 are disposed at substantially the same position in the front-rear direction.
- a gear 106 is attached to the left end portion of the shaft 105.
- the gear 106 meshes with a gear 104 attached to the right end portion of the kick shaft 102.
- a ratchet 107 and a gear 108 are provided at the right end of the shaft 105.
- the ratchet 107 cannot rotate with respect to the shaft 105.
- the ratchet 107 can be displaced in the axial direction of the shaft 105 with respect to the shaft 105.
- the gear 108 can rotate with respect to the shaft 105.
- the gear 108 meshes with a gear 110 provided at the left end portion of the balancer shaft 109 so as not to rotate. Further, the balancer shaft 109 is provided with a gear 111 so as not to rotate. The gear 111 meshes with a gear 118 that is provided on the crankshaft 34 so as not to rotate.
- the ratchet 107 and the gear 108 are not meshed with each other.
- the shaft 105 rotates.
- the ratchet 107 is displaced to the right.
- the ratchet 107 and the gear 108 mesh.
- the rotation of the kick shaft 102 is transmitted to the gear 108.
- the rotation of the kick pedal 24 is transmitted to the crankshaft 34 via the shafts 102, 105, 109 and the gears 104, 106, 107, 108, 110, 111, 118.
- the cell motor 101 is disposed on the upper side and slightly in front of the axis C ⁇ b> 1 of the crankshaft 34.
- a gear 101 a is formed on the rotation shaft of the cell motor 101.
- the gear 101a meshes with a gear 99a provided on the shaft 99 so as not to rotate.
- the shaft 99 is provided with a gear 99b that cannot rotate.
- the gear 99b meshes with a gear 114 that is provided on the crankshaft 34 so as not to rotate. Accordingly, the rotation of the cell motor 101 is transmitted to the crankshaft 34 through the gears 101a, 99a, 99b, 114 and the shaft 99.
- a generator 45 is attached to the left end portion of the crankshaft 34.
- the generator 45 includes an inner 45a and an outer 45b.
- the inner 45a is attached to the crankcase 32 so as not to rotate.
- the outer 45 b is attached to the left end portion of the crankshaft 34.
- the outer 45b rotates together with the crankshaft 34. Therefore, when the crankshaft 34 rotates, the outer 45b rotates relative to the inner 45a. As a result, power generation is performed.
- a transmission cover 50 is attached to the left side of the crankcase 32.
- a transmission chamber 51 is defined by the transmission cover 50 and the crankcase 32.
- a stepped automatic transmission 31 is disposed in the transmission chamber 51.
- the stepped automatic transmission 31 is a 4-speed stepped automatic transmission.
- the stepped automatic transmission 31 is a so-called gear train type stepped automatic transmission that is driven from the input shaft 52 to the output shaft 33 through a plurality of transmission gear pairs.
- the input shaft 52 and the crankshaft 34 of the stepped automatic transmission 31 are constituted by the same rotating shaft.
- the present invention is not limited to this configuration.
- each of the input shaft 52 and the crankshaft 34 may be constituted by different rotating shafts.
- the input shaft 52 and the crankshaft 34 may be arranged on the same axis or may be arranged on different axes.
- a first rotating shaft 53, a second rotating shaft 54, a third rotating shaft 64, A total of five rotation shafts including a fourth rotation shaft 40 and a fifth rotation shaft 41 are provided on the power transmission path between the input shaft 52 and the output shaft 33.
- the input shaft 52, the first rotating shaft 53, the second rotating shaft 54, the third rotating shaft 64, the fourth rotating shaft 40, the fifth rotating shaft 41, and the output shaft 33 are Are arranged substantially parallel to each other.
- the axis C2 of the first rotating shaft 53 is located behind the axis C1 of the input shaft 52. Further, the axis C2 of the first rotating shaft 53 is located below the axis C1 of the input shaft 52. The axis C2 of the first rotating shaft 53 is located slightly below the plane P including the axis C1 of the input shaft 52 and the axis C7 of the output shaft 33.
- the axis C3 of the second rotating shaft 54 is located behind the axis C1 of the input shaft 52 and the axis C2 of the first rotating shaft 53.
- the axis C3 of the second rotation shaft 54 is located above the axis C1 of the input shaft 52 and the axis C2 of the first rotation shaft 53.
- the axis C3 of the second rotation shaft 54 is located above the plane P.
- the axis C4 of the third rotating shaft 64 is located behind the axis C1 of the input shaft 52, the axis C2 of the first rotating shaft 53, and the axis C3 of the second rotating shaft 54. ing.
- the axis C4 of the third rotating shaft 64 is located slightly above the axis C1 of the input shaft 52 and the axis C2 of the first rotating shaft 53.
- the axis C4 of the third rotation shaft 64 is located below the axis C3 of the second rotation shaft 54.
- the axis C4 of the third rotation shaft 64 is located above the plane P.
- the axis C5 of the fourth rotating shaft 40 includes the axis C1 of the input shaft 52, the axis C2 of the first rotating shaft 53, the axis C3 of the second rotating shaft 54, and the axes of the third rotating shaft 64. It is located behind each of the hearts C4.
- the axis C5 of the fourth rotating shaft 40 is located slightly above the axis C1 of the input shaft 52 and the axis C2 of the first rotating shaft 53.
- the axis C5 of the fourth rotating shaft 40 is located below the axis C3 of the second rotating shaft 54.
- the axis C5 of the fourth rotating shaft 40 is located at substantially the same height as the axis C4 of the third rotating shaft 64.
- the axis C5 of the fourth rotation shaft 40 is located above the plane P.
- the axis C6 of the fifth rotating shaft 41 includes the axis C1 of the input shaft 52, the axis C2 of the first rotating shaft 53, the axis C3 of the second rotating shaft 54, and the axes of the third rotating shaft 64. It is located on the rear side of each of the center C4 and the axis C5 of the fourth rotating shaft 40.
- the axis C6 of the fifth rotation shaft 41 is located slightly above the axis C1 of the input shaft 52 and the axis C2 of the first rotation shaft 53.
- the axis C6 of the fifth rotating shaft 41 is positioned below the axis C3 of the second rotating shaft 54, the axis C4 of the third rotating shaft 64, and the axis C5 of the fourth rotating shaft 40. is doing.
- the axis C6 of the fifth rotation shaft 41 is located above the plane P.
- FIG. 6 shows a gear configuration of the stepped automatic transmission 31.
- FIG. 6 schematically shows the gear configuration of the stepped automatic transmission 31. Therefore, the size of the gear and clutch shown in FIG. 6 is different from the actual size.
- the input shaft 52 is provided with an upstream clutch group 81.
- the upstream clutch group 81 includes a first clutch 55 and a third clutch 59.
- the first clutch 55 is disposed on the right side of the third clutch 59.
- the first clutch 55 and the third clutch 59 are each constituted by a centrifugal clutch.
- the first clutch 55 and the third clutch 59 may be clutches other than the centrifugal clutch.
- the first clutch 55 and the third clutch 59 may be hydraulic clutches.
- the first clutch 55 is preferably a centrifugal clutch.
- the first clutch 55 and the third clutch 59 are each constituted by a drum-type centrifugal clutch.
- the first clutch 55 and the third clutch 59 may each be constituted by a multi-plate clutch.
- the first clutch 55 includes an inner 56 as an input side clutch member and an outer 57 as an output side clutch member.
- the inner 56 is provided so as not to rotate with respect to the input shaft 52. For this reason, the inner 56 rotates with the rotation of the input shaft 52.
- the outer 57 is rotatable with respect to the input shaft 52. When the rotational speed of the input shaft 52 becomes higher than a predetermined rotational speed, the inner 56 and the outer 57 come into contact with each other due to the centrifugal force acting on the inner 56. As a result, the first clutch 55 enters the connected state.
- a first gear 58 is provided on the outer 57 of the first clutch 55 so as not to rotate with respect to the outer 57.
- the first gear 58 rotates together with the outer 57 of the first clutch 55.
- the first rotating shaft 53 is provided with a second gear 63.
- the second gear 63 meshes with the first gear 58.
- the first gear 58 and the second gear 63 constitute a first transmission gear pair 86.
- the first transmission gear pair 86 constitutes a first-speed transmission gear pair.
- the second gear 63 is a so-called one-way gear. Specifically, the second gear 63 transmits the rotation of the first gear 58 to the first rotation shaft 53. On the other hand, the second gear 63 does not transmit the rotation of the first rotation shaft 53 to the input shaft 52. Specifically, the second gear 63 also has a one-way rotation transmission mechanism 96.
- the third clutch 59 includes an inner 60 as an output side clutch member and an outer 61 as an input side clutch member.
- a ninth gear 62 is provided in the inner 60 as an output side clutch member of the third clutch 59.
- the ninth gear 62 rotates together with the inner 60.
- a tenth gear 65 is provided on the first rotating shaft 53.
- the tenth gear 65 meshes with the ninth gear 62.
- the tenth gear 65 and the ninth gear 62 constitute a third transmission gear pair 83.
- the third transmission gear pair 83 has a gear ratio different from that of the first transmission gear pair 86.
- the third transmission gear pair 83 has a gear ratio smaller than the gear ratio of the first transmission gear pair 86.
- the third transmission gear pair 83 constitutes a second speed transmission gear pair.
- the inner 60 is provided so as not to rotate with respect to the ninth gear 62.
- the rotation is transmitted to the inner 60 via the first transmission gear pair 86, the first rotation shaft 53, and the third transmission gear pair 83.
- the inner 60 rotates with the rotation of the input shaft 52.
- the outer 61 is rotatable with respect to the input shaft 52.
- the rotational speed of the input shaft 52 becomes higher than a predetermined rotational speed, the inner 60 and the outer 61 come into contact with each other due to the centrifugal force acting on the inner 60.
- the third clutch 59 enters a connected state.
- the outer 57 and the outer 61 are composed of the same member.
- the present invention is not limited to this configuration.
- the outer 57 and the outer 61 may be configured by different members.
- the rotational speed of the input shaft 52 when the first clutch 55 is connected is different from the rotational speed of the input shaft 52 when the third clutch 59 is connected. Specifically, the rotational speed of the input shaft 52 when the first clutch 55 is connected is lower than the rotational speed of the input shaft 52 when the third clutch 59 is connected. More specifically, the first clutch 55 is connected when the rotational speed of the input shaft 52 is equal to or higher than the first rotational speed. On the other hand, the first clutch 55 is in a disconnected state when the rotational speed of the input shaft 52 is less than the first rotational speed. The third clutch 59 is in a connected state when the rotational speed of the input shaft 52 is equal to or higher than the second rotational speed higher than the first rotational speed. On the other hand, the third clutch 59 enters a disconnected state when the rotational speed of the input shaft 52 is less than the second rotational speed.
- the first clutch 55 and the third clutch 59 are located between the first transmission gear pair 86 and the third transmission gear pair 83 in the vehicle width direction. .
- the tenth gear 65 also has a function as the third gear 87.
- a fourth gear 75 is provided on the second rotating shaft 54 so as not to rotate with respect to the second rotating shaft 54.
- the fourth gear 75 rotates together with the second rotation shaft 54.
- the third gear 87 that also functions as the tenth gear 65 meshes with the fourth gear 75.
- the third gear 87 that also functions as the tenth gear 65 and the fourth gear 75 constitute a first transmission gear pair 84.
- the first power transmission mechanism 26 is configured by the first transmission gear pair 84, the first transmission gear pair 86, and the third transmission gear pair 83.
- the rotation of the input shaft 52 is transmitted to the second rotation shaft 54 by the first power transmission mechanism 26.
- a fifth gear 74 is provided on the second rotating shaft 54 so as not to rotate with respect to the second rotating shaft 54.
- the fifth gear 74 rotates together with the second rotation shaft 54.
- a sixth gear 78 is provided on the third rotating shaft 64 so as not to rotate with respect to the third rotating shaft 64.
- the third rotating shaft 64 rotates together with the sixth gear 78.
- the fifth gear 74 and the sixth gear 78 mesh with each other.
- the fifth gear 74 and the sixth gear 78 constitute a second transmission gear pair 85.
- the sixth gear 78 is a so-called one-way gear. Specifically, the sixth gear 78 transmits the rotation of the second rotation shaft 54 to the third rotation shaft 64. On the other hand, the sixth gear 78 does not transmit the rotation of the third rotation shaft 64 to the second rotation shaft 54. Specifically, the sixth gear 78 includes a one-way rotation transmission mechanism 93.
- the sixth gear 78 is a so-called one-way gear.
- the sixth gear 78 may be a normal gear and the fifth gear 74 may be a so-called one gear.
- the fifth gear 74 may be provided with a one-way rotation transmission mechanism. Specifically, the fifth gear 74 transmits the rotation of the second rotation shaft 54 to the sixth gear 78, while the rotation of the sixth gear 78 is not transmitted to the second rotation shaft 54. Also good.
- Downstream clutch group 82 A downstream clutch group 82 is provided on the second rotating shaft 54.
- the downstream clutch group 82 is located behind the upstream clutch group 81.
- the downstream clutch group 82 and the upstream clutch group 81 are arranged at positions where at least a part thereof overlaps in the axial direction of the input shaft 52. Specifically, the downstream clutch group 82 and the upstream clutch group 81 are arranged at positions that substantially overlap in the vehicle width direction.
- the front end 70 b of the second clutch 70 is positioned in front of the rear end 55 a of the first clutch 55.
- the front end of the downstream clutch group 82 is more forward than the rear end of the upstream clutch group 81 when viewed from the axial direction of the input shaft 52. positioned.
- the downstream clutch group 82 includes a second clutch 70 and a fourth clutch 66.
- the fourth clutch 66 is disposed on the right side of the second clutch 70.
- the first clutch 55 and the fourth clutch 66 are arranged so that at least a part thereof overlaps in the vehicle width direction.
- the third clutch 59 and the second clutch 70 are also arranged so that at least a part thereof overlaps in the vehicle width direction.
- the first clutch 55 and the fourth clutch 66 are disposed so as to substantially overlap in the vehicle width direction.
- the third clutch 59 and the second clutch 70 are also arranged so as to substantially overlap in the vehicle width direction.
- the second clutch 70 and the fourth clutch 66 are each constituted by a so-called hydraulic clutch. Specifically, in the present embodiment, the second clutch 70 and the fourth clutch 66 are each constituted by a multi-plate hydraulic clutch. However, the present invention is not limited to this configuration.
- the fourth clutch 66 and the second clutch 70 may be clutches other than the hydraulic clutch.
- the fourth clutch 66 and the second clutch 70 may be centrifugal clutches.
- the fourth clutch 66 and the second clutch 70 are preferably hydraulic clutches.
- the rotational speed of the second rotary shaft 54 when the second clutch 70 is connected is different from the rotational speed of the second rotary shaft 54 when the fourth clutch 66 is connected.
- the rotation speed of the second rotation shaft 54 when the second clutch 70 is connected is the second rotation shaft when the fourth clutch 66 is connected.
- the rotation speed is lower than 54.
- the second clutch 70 includes an inner 71 as an input side clutch member and an outer 72 as an output side clutch member.
- the inner 71 is provided so as not to rotate with respect to the second rotating shaft 54. For this reason, the inner 71 rotates with the rotation of the second rotating shaft 54.
- the outer 72 is rotatable with respect to the second rotation shaft 54. In a state where the second clutch 70 is not connected, when the second rotating shaft 54 rotates, the inner 71 rotates with the second rotating shaft 54, while the outer 72 does not rotate with the second rotating shaft 54. In a state where the second clutch 70 is connected, both the inner 71 and the outer 72 rotate together with the second rotating shaft 54.
- a seventh gear 73 is attached to the outer 72 as an output side clutch member of the second clutch 70.
- the seventh gear 73 rotates together with the outer 72.
- an eighth gear 77 is provided on the third rotating shaft 64 so as not to rotate with respect to the third rotating shaft 64.
- the eighth gear 77 rotates together with the third rotation shaft 64.
- the seventh gear 73 and the eighth gear 77 mesh with each other. Therefore, the rotation of the outer 72 is transmitted to the third rotating shaft 64 via the seventh gear 73 and the eighth gear 77.
- the seventh gear 73 and the eighth gear 77 constitute a second transmission gear pair 91.
- the second transmission gear pair 91 has a gear ratio different from the gear ratio of the first transmission gear pair 86, the gear ratio of the third transmission gear pair 83, and the gear ratio of the fourth transmission gear pair 90. .
- the second transmission gear pair 91 is located on the same side as the side on which the third transmission gear pair 83 is located with respect to the third clutch 59 with respect to the second clutch 70. Specifically, the second transmission gear pair 91 is located on the left side with respect to the second clutch 70. Similarly, the third transmission gear pair 83 is located on the left side with respect to the third clutch 59.
- the second transmission gear pair 91 and the third transmission gear pair 83 are arranged so that at least a part thereof overlaps in the vehicle width direction. Specifically, the second transmission gear pair 91 and the third transmission gear pair 83 are disposed so as to substantially overlap in the vehicle width direction.
- the fourth clutch 66 includes an inner 67 as an input side clutch member and an outer 68 as an output side clutch member.
- the inner 67 is provided so as not to rotate with respect to the second rotating shaft 54. For this reason, the inner 67 rotates with the rotation of the second rotating shaft 54.
- the outer 68 is rotatable with respect to the second rotation shaft 54. In a state where the fourth clutch 66 is not connected, when the second rotating shaft 54 rotates, the inner 67 rotates with the second rotating shaft 54, while the outer 68 does not rotate with the second rotating shaft 54. In a state where the fourth clutch 66 is connected, both the inner 67 and the outer 68 rotate together with the second rotating shaft 54.
- An eleventh gear 69 is attached to the outer 68 as an output side clutch member of the fourth clutch 66.
- the eleventh gear 69 rotates together with the outer 68.
- a twelfth gear 76 is provided on the third rotating shaft 64 so as not to rotate with respect to the third rotating shaft 64.
- the twelfth gear 76 rotates together with the third rotation shaft 64.
- the eleventh gear 69 and the twelfth gear 76 mesh with each other. Therefore, the rotation of the outer 68 is transmitted to the third rotating shaft 64 via the eleventh gear 69 and the twelfth gear 76.
- the twelfth gear 76 and the eleventh gear 69 constitute a fourth transmission gear pair 90.
- the fourth transmission gear pair 90 has a gear ratio different from the gear ratio of the first transmission gear pair 86 and the gear ratio of the third transmission gear pair 83.
- the second clutch 70 and the fourth clutch 66 are located between the second transmission gear pair 91 and the fourth transmission gear pair 90 in the vehicle width direction.
- the fourth transmission gear pair 90 is located on the same side as the side on which the first transmission gear pair 86 is located with respect to the first clutch 55 with respect to the fourth clutch 66. Specifically, the fourth transmission gear pair 90 is located on the right side with respect to the fourth clutch 66. Similarly, the first transmission gear pair 86 is located on the right side with respect to the first clutch 55.
- the fourth transmission gear pair 90 and the first transmission gear pair 86 are arranged so that at least a part thereof overlaps in the vehicle width direction.
- the fourth transmission gear pair 90 and the first transmission gear pair 86 are arranged so that at least a part thereof overlaps with respect to the axial direction of the input shaft 52.
- the fourth transmission gear pair 90 and the first transmission gear pair 86 are disposed so as to substantially overlap in the vehicle width direction.
- the third rotating shaft 64 is provided with a thirteenth gear 79 that cannot rotate with respect to the third rotating shaft 64.
- the thirteenth gear 79 rotates with the third rotation shaft 64.
- a fourteenth gear 80 is provided on the fourth rotating shaft 40 so as not to rotate with respect to the fourth rotating shaft 40.
- the fourteenth gear 80 and the thirteenth gear 79 constitute a third transmission gear pair 98.
- a fifteenth gear 115 is provided on the fourth rotating shaft 40 so as not to rotate.
- the fifteenth gear 115 is engaged with a seventeenth gear 117 provided on the output shaft 33 through a sixteenth gear 116 provided non-rotatably on the fifth rotary shaft 41.
- the rotation of the fourth rotating shaft 40 is transmitted to the output shaft 33 by the fourth transmission gear pair 120 constituted by the fifteenth gear 115, the sixteenth gear 116 and the seventeenth gear 117.
- the fourth transmission gear pair 120, the fourth transmission gear pair 90, the second transmission gear pair 91, the third transmission gear pair 98, and the second transmission gear pair 85 provide the second power.
- a transmission mechanism 27 is configured.
- the rotation of the second rotating shaft 54 is transmitted to the output shaft 33 by the second power transmission mechanism 27.
- downstream clutch group 82 will be described in more detail with reference mainly to FIG.
- the second clutch 70 is provided with a plate group 136.
- the plate group 136 includes a plurality of friction plates 134 and a plurality of clutch plates 135.
- the plurality of friction plates 134 and the plurality of clutch plates 135 are alternately arranged in the vehicle width direction.
- the friction plate 134 cannot rotate with respect to the outer 72.
- the clutch plate 135 cannot rotate with respect to the inner 71.
- the inner 71 is rotatable with respect to the outer 72.
- a pressure plate 163 is arranged on the opposite side of the inner 71 from the outer 72 in the vehicle width direction.
- the pressure plate 163 is urged to the right in the vehicle width direction by the compression coil spring 92. That is, the pressure plate 163 is biased toward the boss 162 by the compression coil spring 92.
- a working chamber 137 is defined between the boss portion 162 and the pressure plate 163.
- the working chamber 137 is filled with oil.
- the pressure plate 163 is displaced in a direction away from the boss portion 162.
- the distance between the pressure plate 163 and the inner 71 is shortened. Therefore, the plate group 136 is brought into a pressure contact state.
- the inner 71 and the outer 72 rotate together, and the second clutch 70 is in a connected state.
- the fourth clutch 66 is provided with a plate group 132.
- the plate group 132 includes a plurality of friction plates 130 and a plurality of clutch plates 131.
- the plurality of friction plates 130 and the plurality of clutch plates 131 are alternately arranged in the vehicle width direction.
- the friction plate 130 cannot rotate with respect to the outer 68.
- the clutch plate 131 cannot rotate with respect to the inner 67.
- the inner 67 can rotate with respect to the outer 68 and can be displaced in the vehicle width direction.
- a pressure plate 161 is arranged on the opposite side of the inner 67 from the outer 68 in the vehicle width direction.
- the pressure plate 161 is urged to the left in the vehicle width direction by a compression coil spring 89. That is, the pressure plate 161 is urged toward the boss 162 by the compression coil spring 89.
- a working chamber 133 is defined between the boss portion 162 and the pressure plate 161.
- the working chamber 133 is filled with oil.
- the pressure plate 161 is displaced in a direction away from the boss portion 162.
- the distance between the pressure plate 161 and the inner 67 is shortened.
- the plate group 132 is brought into a pressure contact state.
- the inner 67 and the outer 68 rotate together, and the fourth clutch 66 is in a connected state.
- minute leak holes 70 a and 66 a communicating with the working chambers 133 and 137 are formed in the second clutch 70 and the fourth clutch 66, respectively. Further, in each of the second clutch 70 and the fourth clutch 66, the inner 71, 67 and the outer 72, 68 are not sealed. Therefore, when the clutches 70 and 66 are disconnected, the oil in the working chambers 133 and 137 can be quickly discharged when the clutch 70 is disconnected. For this reason, according to this embodiment, the responsiveness of the clutches 70 and 66 can be improved. Further, lubrication of other sliding portions is achieved by the oil scattered from the leak holes 70a and 66a or the gap between the inner 71 and the outer 72.
- the working chamber 133 of the fourth clutch 66 and the working chamber 137 of the second clutch 70 are stored in an oil reservoir 99 provided at the bottom of the crank chamber 35 by an oil pump 140. Supplied oil is supplied.
- a strainer 141 is immersed in the oil reservoir 99.
- the strainer 141 is connected to the oil pump 140. By driving the oil pump 140, the oil stored in the oil reservoir 99 is sucked up through the strainer 141.
- a first oil path 144 is connected to the oil pump 140.
- An oil cleaner 142 and a relief valve 147 are provided in the middle of the first oil path 144. The sucked oil is purified by the oil cleaner 142. Further, the relief valve 147 prevents the pressure in the first oil path 144 from exceeding a predetermined pressure.
- the first oil path 144 is connected to the crankshaft 34 and the cylinder head 42. Oil from the oil pump 140 is supplied to the crankshaft 34 and the sliding portion in the cylinder head 42 via the first oil path 144.
- the first oil path 144 is connected to the second oil path 145 and the third oil path 146.
- the second oil path 145 is connected from the valve 143 to the right end portion of the second rotating shaft 54 via the crankcase 32 side shown in FIG.
- the second oil path 145 reaches the working chamber 133 from the right end portion of the second rotating shaft 54 via the inside of the second rotating shaft 54. Therefore, the oil from the oil pump 140 is supplied to the working chamber 133 of the fourth clutch 66 via the first oil path 144 and the second oil path 145.
- the third oil path 146 is connected to the left end portion of the second rotating shaft 54 from the valve 143 through the transmission cover 50 side.
- the third oil path 146 reaches the working chamber 137 from the left end portion of the second rotating shaft 54 via the inside of the second rotating shaft 54. Therefore, the oil from the oil pump 140 is supplied to the working chamber 137 of the second clutch 70 via the first oil path 144 and the third oil path 146.
- the lubricating oil for the engine unit 20 is also used as the hydraulic oil for the second and fourth clutches 70 and 66.
- the connection between the second oil path 145 and the third oil path 146 and the first oil path 144 is performed by a valve 143.
- a motor 150 is attached to the valve 143.
- the valve 143 is driven by the motor 150. Accordingly, the second oil path 145 and the third oil path 146 and the first oil path 144 are intermittently connected. As a result, the second clutch 70 and the fourth clutch 66 are engaged / disengaged.
- the valve 143 includes an outer 143a constituted by the transmission cover 50 and an inner 143b.
- a cylindrical recess 143c is formed in the outer 143a.
- the recess 143c opens toward the outside of the stepped automatic transmission 31.
- a first oil path 144 as a hydraulic oil supply path and second and third oil paths 145 and 146 as hydraulic oil discharge paths are opened on the inner peripheral surface of the recess 143c.
- the inner 143b is formed in a substantially cylindrical shape.
- the inner 143b is rotatably inserted into the recess 143c.
- Communication paths 148 and 149 are formed in the inner 143b.
- the communication path 148 and the communication path 149 are arranged at different positions in the axial direction of the inner 143b.
- the communication path 148 and the communication path 149 are formed independently of each other. That is, the communication path 148 and the communication path 149 are not in communication.
- Both end portions of the communication paths 148 and 149 are open to the outer peripheral surface of the inner 143b.
- the communication path 148 is a path for communicating the first oil path 144 and the second oil path 145.
- the communication path 148 communicates the first oil path 144 and the second oil path 145 when the inner 143b is positioned at the second communication angle with respect to the outer 143a.
- the communication path 149 is a path for communicating the first oil path 144 and the third oil path 146.
- the communication path 149 connects the first oil path 144 and the third oil path 146 when the inner 143b is positioned at the first communication angle with respect to the outer 143a.
- the first communication angle and the second communication angle are different from each other.
- a motor 150 as a drive mechanism is connected to the inner 143b.
- the motor 150 arbitrarily controls the rotation angle of the inner 143b with respect to the outer 143a.
- An ECU 138 as a control unit is connected to the motor 150.
- a vehicle speed sensor 88, a throttle opening sensor 112, and a memory 113 are connected to the ECU 138.
- the throttle opening sensor 112 detects the throttle opening.
- the vehicle speed sensor 88 detects the vehicle speed.
- the inner 143b is provided with a potentiometer (not shown). The angle of the inner 143b is detected by this potentiometer. This potentiometer is also connected to the ECU 138.
- the ECU 138 controls the motor 150 based on at least one of the throttle opening and the vehicle speed. In the present embodiment, the ECU 138 controls the motor 150 based on both the throttle opening and the vehicle speed. Specifically, the ECU 138 calculates the target angle of the inner 143b by applying the throttle opening and the vehicle speed to the VN diagram read from the memory 113. The ECU 138 controls the motor 150 based on the calculated target angle and the current angle of the inner 143b detected by the potentiometer.
- each of the second oil path 145 and the third oil path 146 is provided. Then, the first oil path 144 is disconnected. Accordingly, each of the second clutch 70 and the fourth clutch 66 is disengaged.
- the third gear 87 rotates together with the first rotation shaft 53.
- the first transmission gear pair 84 also rotates as the first rotating shaft 53 rotates. Therefore, the rotation of the first rotation shaft 53 is transmitted to the second rotation shaft 54 via the first transmission gear pair 84.
- the fifth gear 74 rotates together with the second rotation shaft 54.
- the second transmission gear pair 85 also rotates with the rotation of the second rotating shaft 54. Therefore, the rotation of the second rotation shaft 54 is transmitted to the third rotation shaft 64 via the second transmission gear pair 85.
- the thirteenth gear 79 rotates together with the third rotation shaft 64.
- the third transmission gear pair 98 also rotates with the rotation of the third rotating shaft 64. Therefore, the rotation of the third rotation shaft 64 is transmitted to the fourth rotation shaft 40 via the third transmission gear pair 98.
- the fifteenth gear 115 rotates together with the fourth rotation shaft 40.
- the fourth transmission gear pair 120 also rotates as the fourth rotating shaft 40 rotates. Therefore, the rotation of the fourth rotation shaft 40 is transmitted to the output shaft 33 via the fourth transmission gear pair 120.
- the tenth gear 65 rotates together with the first rotation shaft 53. Therefore, at the first speed, the third transmission gear pair 83 and the inner 60 of the third clutch 59 also rotate. However, at the first speed, the third clutch 59 is in a disconnected state. For this reason, the rotation of the input shaft 52 is not transmitted to the first rotating shaft 53 via the third transmission gear pair 83.
- both the second transmission gear pair 91 and the fourth transmission gear pair 90 rotate together with the third rotation shaft 64. Therefore, at the first speed, both the second transmission gear pair 91 and the fourth transmission gear pair 90 rotate. However, at the first speed, each of the second clutch 70 and the fourth clutch 66 is in a disconnected state. For this reason, the rotation of the second rotating shaft 54 is not transmitted to the third rotating shaft 64 via the second transmission gear pair 91 and the fourth transmission gear pair 90.
- the gear ratio of the third transmission gear pair 83 is smaller than the gear ratio of the first transmission gear pair 86. Therefore, the rotation speed of the tenth gear 65 is faster than the rotation speed of the second gear 63. Therefore, the rotation is transmitted from the input shaft 52 to the first rotating shaft 53 via the third transmission gear pair 83. On the other hand, the rotation of the first rotation shaft 53 is not transmitted to the input shaft 52 by the one-way rotation transmission mechanism 96.
- the transmission of the rotational force from the first rotation shaft 53 to the output shaft 33 is performed in the same manner as in the first speed, the first transmission gear pair 84, the second transmission gear pair 85, the third transmission gear pair 98, and This is done via the fourth transmission gear pair 120.
- the third clutch 59, the third transmission gear pair 83, the first transmission gear pair 84, the second transmission gear pair 85, and the third transmission are provided.
- the rotation is transmitted from the input shaft 52 to the output shaft 33 through the gear pair 98 and the fourth transmission gear pair 120.
- the rotational speed of the eighth gear 77 of the second transmission gear pair 91 is higher than the rotational speed of the sixth gear 78 of the third transmission gear pair 83. Therefore, the rotation of the second rotation shaft 54 is transmitted to the third rotation shaft 64 via the second transmission gear pair 91. On the other hand, the rotation of the third rotation shaft 64 is not transmitted to the second rotation shaft 54 by the one-way rotation transmission mechanism 93.
- the rotation of the third rotation shaft 64 is transmitted to the output shaft 33 through the third transmission gear pair 98 and the fourth transmission gear pair 120 in the same manner as in the first speed and the second speed.
- the third clutch 59 the third transmission gear pair 83, the first transmission gear pair 84, the second clutch 70, and the second transmission gear pair. 91, the rotation is transmitted from the input shaft 52 to the output shaft 33 via the third transmission gear pair 98 and the fourth transmission gear pair 120.
- Rotation of the third rotating shaft 64 is transmitted to the output shaft 33 via the third transmission gear pair 98 and the fourth transmission gear pair 120 as in the case of the first speed to the third speed.
- the second rotation shaft 54 is arranged at a position higher than the input shaft 52.
- the second clutch The front end 70 b of the 70 is positioned in front of the rear end 55 a of the first clutch 55. Therefore, the distance between the first clutch 55 and the second clutch 70, which are heavy objects, can be shortened in the front-rear direction. Therefore, in the stepped automatic transmission 31, the engine unit 20, and the motorcycle 1, the mass can be concentrated in the front-rear direction.
- the input is performed while the motorcycle 1 is stationary as in the present embodiment. It is preferable that the front end of the downstream clutch group 82 is positioned in front of the rear end of the upstream clutch group 81 when viewed from the axial direction of the shaft 52. According to this, mass concentration can be more effectively achieved.
- the stepped automatic transmission 31 is a unit swing type. For this reason, for example, when the mass is not concentrated and the center of gravity is located on the rear side, the rigidity required for the pivot shaft 25 and the engine bracket 21 is increased. Therefore, the weight of the stepped automatic transmission 31 tends to increase.
- the mass is concentrated, and the center of gravity of the stepped automatic transmission 31 is configured to be located on the front side. For this reason, the rigidity required for the pivot shaft 25 and the engine bracket 21 is low. Therefore, the stepped automatic transmission 31 can be reduced in weight.
- the center of gravity of the stepped automatic transmission 31 is located on the front side.
- the moment of inertia acting on the stepped automatic transmission 31 can be reduced. Therefore, the rigidity required for the pivot shaft 25 and the engine bracket 21 can be further reduced. Therefore, the stepped automatic transmission 31 can be further reduced in weight.
- stepped automatic transmission 31 is a unit swing type
- so-called unsprung load can be reduced by concentrating the mass.
- Second Embodiment In the first embodiment, the case where power transmission between the input shaft 52 and the output shaft 33 is performed only by a plurality of gear pairs has been described. However, power transmission between the input shaft 52 and the output shaft 33 may be performed by a power transmission mechanism other than the gear pair. For example, a chain may be used for power transmission in at least a part of the power transmission path between the input shaft 52 and the output shaft 33.
- a chain 121 may be used as a part of the second power transmission mechanism 27. Specifically, in the example shown in FIG. 13, a chain 121 is wound around a fifteenth gear 115 and a seventeenth gear 117. By doing so, the 5th rotating shaft 41 and the 16th gear 116 shown in FIG. 6 become unnecessary. Therefore, the number of parts of the transmission can be reduced.
- power transmission between the input shaft 52 and any of the first to fifth rotating shafts 53, 54, 64, 40, 41 may be performed by a chain.
- the mounting center of the engine bracket 21 is located below the axis C1 of the input shaft 52 .
- the positional relationship between the mounting center of the engine bracket 21 and the axis C1 of the input shaft 52 is not particularly limited.
- the attachment center of the engine bracket 21 may be located above the axis C1 of the input shaft 52.
- the mounting center of the engine bracket 21 may be located at substantially the same height as the axis C1 of the input shaft 52.
- the transmission is a unit swing type.
- the transmission is not limited to the unit swing type.
- the transmission may be fixed to the vehicle body frame so as not to be displaced.
- the first rotating shaft 53 is located at a position where the axis C2 of the first rotating shaft 53 is lower than the axis C4 of the third rotating shaft 64.
- the example arranged so is described.
- the present invention is not limited to this configuration.
- the first rotation shaft 53 may be arranged so that the axis C2 of the first rotation shaft 53 is located lower than the axis C4 of the third rotation shaft 64.
- the first rotation shaft 53 may be arranged so that the axis C2 of the first rotation shaft 53 is located below the plane P.
- the third rotation shaft 64 may be arranged such that the axis C4 of the third rotation shaft 64 is located below the plane P.
- both the cell motor and the kick starter are provided.
- both the cell motor and the kick starter are not necessarily provided. Only one of the cell motor and the kick starter may be provided.
- the present invention is not limited to this configuration.
- the unidirectional rotation transmission mechanism 93 may be disposed with respect to the fifth gear 74.
- the present invention is not limited to this configuration.
- the unidirectional rotation transmission mechanism 96 may be disposed with respect to the first gear 58.
- the present invention is not limited to this.
- the first clutch 55 may be disposed on the left side with respect to the first transmission gear pair 86
- the third clutch 59 may be disposed on the left side with respect to the third transmission gear pair 83.
- the second clutch 70 and the fourth clutch 66 are arranged between the second transmission gear pair 91 and the fourth transmission gear pair 90 .
- the present invention is not limited to this.
- the second clutch 70 may be disposed on the left side with respect to the second transmission gear pair 91
- the fourth clutch 66 may be disposed on the left side with respect to the fourth transmission gear pair 90.
- the preferred embodiment in which the present invention is implemented has been described by taking the 4-speed stepped automatic transmission 31 as an example.
- the present invention is not limited to this.
- the stepped automatic transmission 31 may be 5th speed or higher.
- the stepped automatic transmission 31 may be a three-speed transmission. Specifically, when configuring a three-speed transmission, it is conceivable that the fourth clutch 66 and the second transmission gear pair 91 of the stepped automatic transmission 31 of FIG. 6 are not provided.
- the stepped automatic transmission 31 may be a two-speed transmission. Specifically, when configuring a two-speed transmission, the third clutch 59, the fourth transmission gear pair 90, the one-way rotation transmission mechanism 96, the fourth clutch of the stepped automatic transmission 31 of FIG. 66 and the second transmission gear pair 91 may be omitted.
- the engine 30 is a single cylinder engine.
- the engine 30 is not limited to a single cylinder engine.
- the engine 30 may be a multi-cylinder engine such as a two-cylinder engine.
- gear pair is meshed directly has been described.
- present invention is not limited to this.
- the gear pair may be meshed indirectly via a separately provided gear.
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Abstract
Description
(発明の効果)
20 エンジンユニット(パワーユニット)
21 エンジンブラケット(取り付け部)
26 第1の動力伝達機構
27 第2の動力伝達機構
28 ケーシング
30 エンジン(パワーソース)
31 有段式自動変速装置
33 出力軸
52 入力軸
54 第2の回転軸(中間軸)
55 第1のクラッチ
59 第3のクラッチ
66 第4のクラッチ
70 第2のクラッチ
70b 第2のクラッチの前端
83 第3の変速ギア対(ギア対)
84 第1の伝達ギア対(ギア対)
85 第2の伝達ギア対(ギア対)
86 第1の変速ギア対(ギア対)
90 第4の変速ギア対(ギア対)
91 第2の変速ギア対(ギア対)
98 第3の伝達ギア対(ギア対)
120 第4の伝達ギア対(ギア対)
121 チェーン
以下、本発明を実施した好ましい形態の一例について、図1に示す自動二輪車1を例に挙げて説明する。本実施形態において説明する自動二輪車1は、スクーターである。但し、本発明において、鞍乗型車両は、スクーターに限定されない。本発明の鞍乗型車両は、ライダーが跨って乗車する車両一般をいう。本発明の鞍乗型車両には、自動二輪車の他に、ATV(All
Terrain Vehicle)なども含まれる。ATVは、オフロードビークル(off-road vehicle)とも呼ばれる。本明細書において、自動二輪車は、前輪及び後輪を有し、車体を傾斜させて進行方向を変化させる車両をいう。自動二輪車には、前輪及び後輪の少なくとも一方が複数の車輪によって構成されているものも含まれる。自動二輪車には、モーターサイクル、モペッド、スクーター、オフロード車などが含まれる。
まず、図1を参照しながら自動二輪車1の概略構成について説明する。尚、以下の説明において、前後左右の方向は、自動二輪車1のシート14に着座したライダーから視た方向をいうものとする。
次に、図2~図8を参照しながらエンジンユニット20の構成について説明する。図2に示すように、エンジンユニット20は、パワーソースとしてのエンジン30と、有段式自動変速装置31とを備えている。
エンジン30は、クランクケース32を備えている。クランクケース32は、後述する変速装置カバー50と、図示しない発電機カバーと共に上記ケーシング28を構成している。
図2に示すように、クランク軸34の左側端部は、発電機45が取り付けられている。発電機45は、インナ45aと、アウタ45bとを備えている。インナ45aは、クランクケース32に対して回転不能に取り付けられている。一方、アウタ45bは、クランク軸34の左側端部に取り付けられている。アウタ45bは、クランク軸34と共に回転する。よって、クランク軸34が回転すると、アウタ45bはインナ45aに対して相対的に回転する。これによって、発電が行われる。
クランクケース32の左側には、変速装置カバー50が取り付けられている。この変速装置カバー50とクランクケース32とによって、変速装置室51が区画形成されている。
図6に有段式自動変速装置31のギア構成を示す。なお、図6は、有段式自動変速装置31のギア構成を模式的に示すものである。従って、図6に示すギアやクラッチの大きさは実際の大きさと異なる。
第2の回転軸54には、下流側クラッチ群82が設けられている。下流側クラッチ群82は上流側クラッチ群81の後方に位置している。下流側クラッチ群82と上流側クラッチ群81とは、入力軸52の軸方向に関して、少なくとも一部が重なる位置に配置されている。詳細には、下流側クラッチ群82と上流側クラッチ群81とは、車幅方向に関して、実質的に重なる位置に配置されている。
次に、主として図7を参照しながら、下流側クラッチ群82についてさらに詳細に説明する。
図8に示すように、第4のクラッチ66の作動室133と、第2のクラッチ70の作動室137とには、オイルポンプ140によって、クランク室35の底部に設けられたオイル溜まり99に溜められたオイルが供給される。
次に有段式自動変速装置31の動作について、図9~図12を参照しながら詳細に説明する。
まず、エンジン30が始動すると、入力軸52と一体に形成されたクランク軸34の回転が開始する。第1のクラッチ55のインナ56は入力軸52と共に回転する。このため、入力軸52の回転速度が所定の第1の回転速度以上になると、図9に示すように、第1のクラッチ55が接続状態となる。第1のクラッチ55が接続状態となると、第1のクラッチ55のアウタ57と共に、第1の変速ギア対86が回転する。これにより、入力軸52の回転が第1の回転軸53に伝達される。
上記1速時において、第3のギア87と共通の第10のギア65は、第1の回転軸53と共に回転している。このため、第10のギア65と噛合する第9のギア62と、第3のクラッチ59のインナ60とも共に回転している。よって、入力軸52の回転速度が上昇すると、第3のクラッチ59のインナ60の回転速度も上昇する。入力軸52の回転速度が上記第1の回転速度よりも速い第2の回転速度以上になると、インナ60の回転速度もその分上昇し、図10に示すように、第3のクラッチ59が接続状態となる。
上記2速時において、入力軸52と一体に形成されたクランク軸34の回転速度が第2の回転速度よりも高くなり、且つ、車速が所定の車速以上になると、図7に示すバルブ143のインナ143bが駆動され、インナ143bの位置が第1の連通角度となる。その結果、第1のオイル経路144と第3のオイル経路146とが連通経路149を介して接続される。よって、図11に示すように、第2のクラッチ70が接続状態となる。ここで、第2の変速ギア対91のギア比は、第2の伝達ギア対85のギア比よりも小さい。このため、第2の変速ギア対91の第8のギア77の回転速度が、第3の変速ギア対83の第6のギア78の回転速度よりも高くなる。このため、第2の回転軸54の回転は、第2の変速ギア対91を介して第3の回転軸64に伝達される。一方、第3の回転軸64の回転は、一方向回転伝達機構93により第2の回転軸54には伝達されない。
上記3速時において、入力軸52と一体に形成されたクランク軸34の回転速度がさらに高くなり、且つ、車速もさらに高くなると、図7に示すバルブ143のインナ143bが駆動され、インナ143bの位置が第2の連通角度となる。その結果、第4のクラッチ66が接続状態となる一方、第2のクラッチ70は切断状態となる。ここで、第4の変速ギア対90のギア比は、第2の伝達ギア対85のギア比よりも小さい。このため、第4の変速ギア対90の第12のギア76の回転速度が、第2の伝達ギア対85の第6のギア78の回転速度よりも高くなる。このため、第2の回転軸54の回転は、第4の変速ギア対90を介して第3の回転軸64に伝達される。一方、第3の回転軸64の回転は、一方向回転伝達機構93により第2の回転軸54には伝達されない。
上記第1の実施形態では、入力軸52と出力軸33との間の動力伝達が複数のギア対のみによって行われる場合について説明した。但し、入力軸52と出力軸33との間の動力伝達は、ギア対以外の動力伝達機構によって行われていてもよい。例えば、入力軸52と出力軸33との間の動力伝達経路の少なくとも一部における動力伝達にチェーンが用いられていてもよい。
上記第1の実施形態では、エンジンブラケット21の取り付け中心が入力軸52の軸心C1よりも下側に位置する場合について説明した。但し、本発明において、エンジンブラケット21の取り付け中心と入力軸52の軸心C1との位置関係は特に限定されない。例えば、エンジンブラケット21の取り付け中心は、入力軸52の軸心C1よりも上側に位置していてもよい。エンジンブラケット21の取り付け中心は、入力軸52の軸心C1と実質的に同じ高さに位置していてもよい。
Claims (11)
- 入力軸と、前記入力軸よりも後方に配置された中間軸と、出力軸とを備える鞍乗型車両用の有段式自動変速装置であって、
前記入力軸の回転速度に応じて断続される第1のクラッチと、
前記第1のクラッチが接続されているときに前記入力軸の回転を前記中間軸に伝達する第1の動力伝達機構と、
前記中間軸に設けられ、前記中間軸の回転速度に応じて断続される第2のクラッチと、
前記第2のクラッチが接続されているときに前記中間軸の回転を前記出力軸に伝達する第2の動力伝達機構と、
を備え、
前記入力軸の軸心方向から視た際に、前記第2のクラッチの前端が前記第1のクラッチの後端よりも前側に位置している鞍乗型車両用の有段式自動変速装置。 - 請求項1に記載された鞍乗型車両用の有段式自動変速装置において、
前記入力軸、前記中間軸、前記出力軸、前記第1及び第2のクラッチ並びに前記第1及び第2の動力伝達機構を収納するケーシングをさらに備え、
前記ケーシングは、前記鞍乗型車両に対して取り付けられる取り付け部を有し、
前記取り付け部において揺動可能に取り付けられる鞍乗型車両用の有段式自動変速装置。 - 請求項2に記載された鞍乗型車両用の有段式自動変速装置において、
前記取り付け部の少なくとも一部は、前記入力軸の軸心よりも前側に位置している鞍乗型車両用の有段式自動変速装置。 - 請求項3に記載された鞍乗型車両用の有段式自動変速装置において、
前記取り付け部の側面視における取り付け中心は、前記入力軸の軸心よりも下側に位置している鞍乗型車両用の有段式自動変速装置。 - 請求項1に記載された鞍乗型車両用の有段式自動変速装置において、
前記第1の動力伝達機構は、前記入力軸の回転を前記中間軸に伝達する1または複数のギア対を有する鞍乗型車両用の有段式自動変速装置。 - 請求項1に記載された鞍乗型車両用の有段式自動変速装置において、
前記第2の動力伝達機構は、前記中間軸の回転を前記出力軸に伝達する1または複数のギア対を有する鞍乗型車両用の有段式自動変速装置。 - 請求項1に記載された鞍乗型車両用の有段式自動変速装置において、
前記第2の動力伝達機構は、前記中間軸の回転を前記出力軸に伝達する1または複数のチェーンを有する鞍乗型車両用の有段式自動変速装置。 - 請求項1に記載された鞍乗型車両用の有段式自動変速装置において、
前記入力軸の回転速度に応じて断続される第3のクラッチをさらに備え、
前記第3のクラッチが接続されるときの前記入力軸の回転速度は、前記第1のクラッチが接続されるときの前記入力軸の回転速度よりも高く、
前記第1の動力伝達機構は、前記第3のクラッチが接続されているときには、前記第1のクラッチが接続されているときよりも小さな変速比で前記入力軸の回転を前記中間軸に伝達する鞍乗型車両用の有段式自動変速装置。 - 請求項1に記載された鞍乗型車両用の有段式自動変速装置において、
前記中間軸の回転速度に応じて断続される第4のクラッチをさらに備え、
前記第4のクラッチが接続されるときの前記中間軸の回転速度は、前記第2のクラッチが接続されるときの前記中間軸の回転速度よりも高く、
前記第2の動力伝達機構は、前記第4のクラッチが接続されているときには、前記第2のクラッチが接続されているときよりも小さな変速比で前記中間軸の回転を前記出力軸に伝達する鞍乗型車両用の有段式自動変速装置。 - 請求項1に記載された鞍乗型車両用の有段式自動変速装置と、
前記入力軸を回転させるパワーソースと、
を備えるパワーユニット。 - 請求項10に記載のパワーユニットを備える鞍乗型車両。
Priority Applications (7)
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AP2011005577A AP2931A (en) | 2008-08-08 | 2009-01-16 | Stepwise automatic transmission for straddle-type vehicle, power unit having the stepwise automatic transmission for straddle-type vehicle, and straddle-type vehicle having the power unit |
MX2011001469A MX2011001469A (es) | 2008-08-08 | 2009-01-16 | Transmision automatica en etapas para un vehiculo del tipo para montar a horcajadas, unidad de potencia que tiene transmision automatica en estapas para el vehiculo del tipo para montar a horcajadas, y vehiculo del tipo para montar a horcajadas que t |
US13/057,801 US8763486B2 (en) | 2008-08-08 | 2009-01-16 | Stepwise automatic transmission for saddle riding type vehicle, power unit equipped with the same, and saddle riding type vehicle equipped with the same |
ES09804648T ES2388574T3 (es) | 2008-08-08 | 2009-01-16 | Transmisión automática paso a paso para vehículo de tipo de montar en sillín, unidad de accionamiento equipada con la misma, y vehículo de tipo de montar en sillín equipado con la misma |
CN200980131027.1A CN102119290B (zh) | 2008-08-08 | 2009-01-16 | 骑乘型车辆用的有级式自动变速装置、具备该装置的动力单元和具备该动力单元的骑乘型车辆 |
EP09804648A EP2309151B1 (en) | 2008-08-08 | 2009-01-16 | Stepwise automatic transmission for saddle riding type vehicle, power unit equipped with the same, and saddle riding type vehicle equipped with the same |
TW098113897A TWI383918B (zh) | 2008-08-08 | 2009-04-27 | 跨坐型車輛用之分段式自動變速裝置,具備該分段式自動變速裝置之動力單元,及具備該動力單元之跨坐型車輛 |
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CO (1) | CO6341665A2 (ja) |
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US9580129B2 (en) * | 2015-05-13 | 2017-02-28 | Burromax LLC | Assembly comprising an internal combustion engine selectively couple to generator and to another mechanically driven device |
ITUB20152778A1 (it) * | 2015-08-03 | 2017-02-03 | Piaggio & C Spa | Cambio sincrono a tre velocita |
CN110573418B (zh) * | 2017-04-03 | 2021-09-10 | Tvs电机股份有限公司 | 用于两轮车辆的传动系统 |
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- 2009-01-16 AP AP2011005577A patent/AP2931A/xx active
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CO6341665A2 (es) | 2011-11-21 |
AP2931A (en) | 2014-06-30 |
EP2309151A4 (en) | 2011-08-17 |
TWI383918B (zh) | 2013-02-01 |
CN102119290A (zh) | 2011-07-06 |
US20110259696A1 (en) | 2011-10-27 |
CN102119290B (zh) | 2014-03-19 |
MX2011001469A (es) | 2011-03-25 |
AP2011005577A0 (en) | 2011-02-28 |
US8763486B2 (en) | 2014-07-01 |
EP2309151A1 (en) | 2011-04-13 |
EP2309151B1 (en) | 2012-06-06 |
TW201008828A (en) | 2010-03-01 |
ES2388574T3 (es) | 2012-10-16 |
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