WO2010016162A1 - 自動二輪車 - Google Patents
自動二輪車 Download PDFInfo
- Publication number
- WO2010016162A1 WO2010016162A1 PCT/JP2009/000140 JP2009000140W WO2010016162A1 WO 2010016162 A1 WO2010016162 A1 WO 2010016162A1 JP 2009000140 W JP2009000140 W JP 2009000140W WO 2010016162 A1 WO2010016162 A1 WO 2010016162A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- transmission
- clutch
- gear
- shaft
- rotation
- Prior art date
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B61/00—Adaptations of engines for driving vehicles or for driving propellers; Combinations of engines with gearing
- F02B61/02—Adaptations of engines for driving vehicles or for driving propellers; Combinations of engines with gearing for driving cycles
-
- 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
- B62K11/00—Motorcycles, engine-assisted cycles or motor scooters with one or two wheels
- B62K11/02—Frames
- B62K11/10—Frames characterised by the engine being over or beside driven rear wheel
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
- B60K17/06—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing
- B60K17/08—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing of mechanical type
-
- 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
- F16H57/027—Gearboxes; Mounting gearing therein characterised by means for venting gearboxes, e.g. air breathers
-
- 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
-
- 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
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/045—Lubricant storage reservoirs, e.g. reservoirs in addition to a gear sump for collecting lubricant in the upper part of a gear case
-
- 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
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0467—Elements of gearings to be lubricated, cooled or heated
- F16H57/0475—Engine and gearing, i.e. joint lubrication or cooling or heating thereof
-
- 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
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/048—Type of gearings to be lubricated, cooled or heated
- F16H57/0493—Gearings with spur or bevel gears
- F16H57/0494—Gearings with spur or bevel gears with variable gear ratio or for reversing rotary motion
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19219—Interchangeably locked
- Y10T74/19251—Control mechanism
- Y10T74/19256—Automatic
- Y10T74/1926—Speed responsive
Definitions
- the present invention relates to a motorcycle, and more particularly, to a motorcycle including an engine unit lubricated with oil.
- the transmission chamber is usually provided with a cooling air inlet for introducing cooling air.
- Patent Document 1 when cooling air is introduced into the transmission chamber, there is a problem that foreign matter is sent into the transmission chamber together with the cooling air.
- a cooling air introduction port 503 is formed in an inner cover 502 disposed below the seat 501, and the cooling air introduction port 503 and the speed change are changed. It has been proposed to connect the device chamber 504 with a hose 505. As described above, by arranging the cooling air introduction port 503 in the space surrounded by the seat 501 and the inner cover 502, the inflow of foreign matter into the transmission chamber 504 is effectively suppressed.
- JP-A-10-299873 JP-A-10-299873
- the hose 505 it may be possible not to provide the hose 505 in order to provide a large storage space. However, in that case, the formation position of the inlet for cooling air is lowered. For this reason, there exists a possibility that a foreign material may mix in a transmission device chamber. Therefore, the durability of the transmission may be reduced.
- the present invention has been made in view of such a point, and an object of the present invention is to provide a motorcycle that has high durability and can form a large space below the seat.
- a motorcycle according to the present invention includes a body frame, an engine unit, drive wheels, a seat, and a cover member.
- the engine unit is suspended in a swingable manner on the body frame.
- the engine unit includes an engine and a stepped automatic transmission.
- the drive wheels are driven by the engine unit.
- the seat is attached to the vehicle body frame so that at least a part thereof is positioned above the engine unit.
- the cover member is attached to the vehicle body frame, and forms at least a part of an internal space located between the seat and the engine unit.
- the engine has a crankcase, a crankshaft, and a cylinder body.
- a crank chamber is defined in the crankcase.
- the crankshaft is housed in the crank chamber.
- the cylinder body is connected to the crankcase.
- a cylinder is formed in the cylinder body. The central axis of the cylinder extends obliquely upward from the crankcase toward the front side.
- the stepped automatic transmission has a transmission case, an input shaft, an output shaft, and a gear pair.
- the transmission case is disposed so that the front portion of the transmission case is adjacent to the crankcase in the vehicle width direction.
- a transmission chamber is defined in the transmission case.
- the input shaft is disposed in the transmission chamber.
- the rotation of the crankshaft is transmitted to the input shaft.
- the output shaft is disposed behind the input shaft in the transmission chamber.
- Drive wheels are attached to the output shaft.
- the plurality of sets of gear pairs are arranged in the transmission chamber.
- the plural pairs of gears transmit the rotation on the input shaft side to the output shaft side.
- the reduction ratios of a plurality of sets of gear pairs are different from each other.
- An oil sump is formed in each of the bottom of the crank chamber and the bottom of the transmission chamber portion located in the front portion of the transmission case. Oil supplied to each sliding portion of the engine and a plurality of sets of gear pairs is stored in the oil reservoir.
- a communication path is formed between the crankcase and the transmission case. The communication path allows an oil reservoir formed in the crankcase and an oil reservoir formed in the transmission case to communicate with each other.
- the bottom surface of the portion of the transmission chamber where the oil sump is formed is located below the bottom surface of the portion behind the oil sump in the transmission chamber.
- a motorcycle having high durability and capable of forming a large space below the seat can be provided.
- FIG. 1 is a left side view of the motorcycle according to the first embodiment.
- FIG. 2 is a left side view of the motorcycle according to the first embodiment.
- 3 is a view taken in the direction of arrows II-II in FIG.
- FIG. 4 is a 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 conceptual diagram showing an oil circuit.
- FIG. 8 is a schematic diagram for explaining a power transmission path at the first speed in the transmission.
- FIG. 9 is a schematic diagram for explaining a power transmission path at the second speed in the transmission.
- FIG. 10 is a schematic diagram for explaining a power transmission path at the third speed in the transmission.
- FIG. 8 is a schematic diagram for explaining a power transmission path at the first speed in the transmission.
- FIG. 9 is a schematic diagram for explaining a power transmission path at the second speed in
- FIG. 11 is a schematic diagram for explaining the power transmission path at the fourth speed in the transmission.
- FIG. 12 is a schematic diagram illustrating a configuration of an engine unit in the second embodiment.
- FIG. 13 is a side view showing a part of the motorcycle disclosed in Patent Document 1. As shown in FIG.
- the motorcycle according to the present invention is not particularly limited as long as it is a motorcycle including a unit swing type engine.
- the motorcycle according to the present invention may be, for example, a moped or a scooter.
- the motorcycle 1 includes a body frame 10.
- the vehicle body frame 10 has a head pipe 10b.
- the head pipe 10b 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 10b.
- 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 as a driven wheel 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.
- the vehicle body cover 13 includes a front cowl 13a, a leg shield 13b, and a side cowl 13c.
- the front cowl 13 a covers the front side of the vehicle body frame 10.
- the leg shield 13b covers the rear side of the head pipe 10b shown in FIG.
- the side cowl 13 c covers the side of the body frame 10.
- a foot step 17 for placing the rider's foot is provided at the side of the side cowl 13c.
- 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.
- a rear wheel 18 as a drive wheel is attached to the output shaft 33 of the engine unit 20.
- 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 in a crankcase 32 that constitutes a part 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.
- 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 C ⁇ b> 1 of the input shaft 52 and below the cylinder body 37.
- 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.
- a seat 14 is disposed above the engine unit 20.
- the front end of the seat 14 and the front end of the engine unit 20 are located at substantially the same position in the front-rear direction. That is, the engine unit 20 is disposed on the rear side of the front end of the seat 14.
- the front end portion of the seat 14 is rotatably attached to the shaft 10a of the body frame 10.
- a cover member 11 attached to the vehicle body frame 10 is disposed between the seat 14 and the engine unit 20.
- the cover member 11 is formed with a storage space 11 a as an internal space located between the seat 14 and the engine unit 20.
- the storage space 11a as an internal space is a storage space for a rider to store a helmet, luggage, and the like.
- the storage space 11a is open upward.
- the upper part of the storage space 11 a is covered with a sheet 14.
- the storage space 11 a can be opened and closed by the rider rotating the seat 14.
- the engine unit 20 includes an engine 30 and a stepped automatic transmission 31.
- the engine 30 includes a crankcase 32.
- the crankcase 32 constitutes the casing 28 together with a transmission case 50 described later.
- the crankcase 32 includes a right casing portion 32a and a left casing portion 32b.
- the right casing part 32a and the left casing part 32b are attached to each other in the vehicle width direction.
- 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 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.
- the cylinder body 37 extends slightly obliquely upward from the crankcase 32 toward the front.
- a cylinder head 42 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 central axis 38a of the cylinder 38 is on a plane P that passes through the axis C1 of the input shaft 52 and the axis C7 of the output shaft 33 of the stepped automatic transmission 31 described later. It is inclined with respect to it. Specifically, in a state where the motorcycle 1 is stationary, the plane P is substantially horizontal, whereas the central axis 38a extends slightly obliquely upward toward the front.
- a transmission case 50 is provided on the left side of the crankcase 32.
- the front portion 50c of the transmission case 50 is disposed so as to be adjacent to the crankcase 32 in the vehicle width direction.
- a portion 50d located rearward of the front portion 50c of the transmission case 50 is located rearward of the crankcase 32 in the front-rear direction.
- the rear portion 50d is located on the left side of the rear wheel 18.
- the transmission case 50 includes a right casing portion 50a and a left casing portion 50b.
- the right casing part 50a and the left casing part 32b are attached in the vehicle width direction.
- a transmission device chamber 51 is defined by the right casing portion 50a and the left casing portion 32b.
- the right casing portion 50a and the left casing portion 32b of the crankcase 32 are configured by a common member.
- the present invention is not limited to this configuration. You may comprise the right casing part 50a and the left casing part 32b by another member.
- 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 C ⁇ b> 2 of the first rotation shaft 53 is located behind the axis C ⁇ b> 1 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 as a first gear pair.
- 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 as a second gear pair.
- 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 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 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.
- the engine unit 20 is provided with an oil reservoir 99. Oil is stored in the oil reservoir 99.
- the oil stored in the oil sump 99 includes the sliding portions of the engine 30, the gear pairs 83 to 86, 90, 91, 96 of the stepped automatic transmission 31, the second and fourth clutches 70, 66.
- the oil sump 99 includes a first oil sump 99a formed at the bottom of the crank chamber 35 and a second oil sump 99b formed at the bottom of the transmission chamber 51.
- the first oil reservoir 99a and the second oil reservoir 99b are communicated with each other by a communication hole 24 as a communication path formed in the left casing portion 32b formed of a member common to the right casing portion 50a. .
- the second oil sump 99 b is formed in the front portion 50 c of the transmission case 50.
- the second oil reservoir 99b is not formed in the rear portion 50d of the transmission case 50.
- the bottom surface of the transmission chamber 51 in the front portion 50c where the second oil reservoir 99b is formed is below the bottom surface of the transmission chamber 51 in the rear portion 50d where the second oil reservoir 99b is not formed. positioned.
- a strainer 141 is immersed in the oil reservoir 99.
- the strainer 141 is connected to the oil pump 140.
- this single oil pump 140 causes each sliding portion of the engine 30, each gear pair 83 to 86, 90, 91, 96 of the stepped automatic transmission 31, and the second and fourth clutches. Oil supply to 70 and 66 is performed.
- 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 portions of the engine 30 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 to the working chamber 137 of the second clutch 70.
- the third oil path 146 is connected to the working chamber 133 of the fourth clutch 66. For this reason, oil is supplied to the second and fourth clutches 70 and 66 through the second and third oil paths 145 and 146.
- a hydraulic pressure switching valve 143 is provided between the first oil path 144 and the second and third oil paths 145 and 146. By the hydraulic pressure switching valve 143, the first oil path 144 and the second and third oil paths 145 and 146 are intermittently connected.
- Leak holes 137a and 133a communicating with the working chambers 137 and 133 are formed in the second clutch 70 and the fourth clutch 66, respectively.
- the oil supplied to the second and fourth clutches 70 and 66 leaks out of the working chambers 137 and 133 from the leak holes 137a and 133a.
- the leaked oil scatters as the second and fourth clutches 70 and 66 rotate and is supplied to the sliding portions of the stepped automatic transmission 31 such as the gear pairs 83 to 86, 90, 91, and 96. Is done.
- 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 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 stepped automatic transmission 31 provided with a plurality of pairs of transmission gears 83, 86, 91, 92 is employed. For this reason, compared with the case where a belt type automatic transmission is adopted, high durability can be realized.
- the stepped automatic transmission 31 provided with a plurality of pairs of transmission gears 83, 86, 91, 92, it is not necessary to introduce cooling air into the transmission chamber 51. For this reason, it is not necessary to provide a duct or the like for introducing cooling air into the transmission device chamber 51.
- the center axis 38a of the cylinder 38 extends obliquely upward toward the front. For this reason, the oil supplied to the cylinder body 37 and the cylinder head 42 is efficiently collected in the oil reservoir 99 via the cylinder 38.
- the bottom surface of the transmission chamber 51 in the front portion 50c is located below the bottom surface of the transmission chamber 51 in the rear portion 50d. For this reason, the oil supplied to each sliding part of the stepped automatic transmission 31 is efficiently recovered in the oil reservoir 99 provided in the front portion 50c. This reduces the amount of oil required.
- the oil supplied to each sliding portion of the engine 30 and the oil supplied to each sliding portion of the stepped automatic transmission 31 are stored in the oil reservoir 99 in common.
- the amount of oil required is reduced as compared with the case where the oil sump for the engine 30 and the oil sump for the stepped automatic transmission 31 are provided separately. Therefore, the capacity of the oil reservoir 99 can be reduced. Accordingly, the height of the oil reservoir 99 can be reduced. Therefore, the height dimension in the front portion 50c of the stepped automatic transmission 31 can be reduced.
- oil supply to each sliding part of the engine 30 and oil supply to each sliding part of the stepped automatic transmission 31 are performed by a common oil pump 140.
- the engine unit 20 can be reduced in size compared with the case where the oil pump for the engine 30 and the oil pump for the stepped automatic transmission 31 are provided separately. Therefore, a larger storage space 11a can be secured.
- the engine bracket 21 as an attachment portion is provided in front of the axis C1 of the crankshaft 34.
- the distance between the engine bracket 21 and the oil reservoir 99 is short. Therefore, the amount of shaking of the oil sump 99 when the engine unit 20 swings with respect to the vehicle body frame 10 can be reduced. Therefore, the depth of the oil reservoir 99 can be further reduced. As a result, the height dimension of the front portion 50c of the stepped automatic transmission 31 can be further reduced. Therefore, a larger storage space 11a can be secured.
- the engine bracket 21 is provided below the cylinder body 37.
- the distance between the engine bracket 21 and the oil reservoir 99 is particularly short. Therefore, the amount of rocking of the oil reservoir 99 can be reduced. For this reason, the oil reservoir 99 can be shallowed.
- the height dimension of the front portion 50c of the stepped automatic transmission 31 can be further reduced. Accordingly, the storage space 11a can be further expanded.
- the axis C3 of the second rotating shaft 54 provided with the second and fourth clutches 70 and 66 is not on the plane P. Specifically, the axis C3 is located above the plane P. For this reason, compared with the case where the axial center C3 is located on the plane P, for example, the second rotating shaft 54 and the second and fourth clutches 70 and 66 can be disposed on the front side. Therefore, the mass of the stepped automatic transmission 31 can be concentrated on the front side. Thereby, the rocking
- 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.
- the chain 121 is wound around the fifteenth gear 115 and the seventeenth gear 117.
- 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 internal space of the cover member 11 is used as the storage space 11a has been described.
- the internal space of the cover member 11 may be used as a space other than the storage space.
- the internal space of the cover member 11 may be used as, for example, an arrangement space for electrical components, a fuel tank, or the like.
- the present invention is not limited to this configuration.
- the axis C3 may be located below the plane P.
- 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.
Abstract
Description
(発明の効果)
10 車体フレーム
11 カバー部材
11a 収納スペース(内部空間)
14 シート
18 後輪(駆動輪)
20 エンジンユニット
21 エンジンブラケット(取り付け部)
24 連通孔(連通経路)
30 エンジン
31 有段式自動変速装置
32 クランクケース
33 出力軸
34 クランク軸
35 クランク室
37 シリンダボディ
38 シリンダ
38a シリンダの中心軸
50 変速装置ケース
50c 前側部分
50d 後側部分
51 変速装置室
52 入力軸
54 第2の回転軸(中間軸)
70 第2のクラッチ(クラッチ)
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、第1のギア対)
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、第2のギア対)
99a 第1のオイル溜まり(クランクケースに形成されたオイル溜まり)
99b 第2のオイル溜まり(変速装置ケースに形成されたオイル溜まり)
140 オイルポンプ
C1 クランクシャフトの軸心(入力軸の軸心)
C3 第2の回転軸の軸心(中間軸の軸心)
C7 出力軸の軸心
P 入力軸の軸心と出力軸の軸心とを含む平面
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。但し、本発明に係る自動二輪車は、ユニットスイングタイプのエンジンを備える自動二輪車である限りにおいて特に限定されない。本発明に係る自動二輪車は、例えば、モペッドやスクーターであってもよい。
まず、図1及び図2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及び図4~図7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4に示すように、エンジンユニット20は、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、後述する変速装置ケース50と共に上記ケーシング28を構成している。
図4に示すように、クランクケース32の左側には、変速装置ケース50が設けられている。詳細には、変速装置ケース50の前側部分50cがクランクケース32と車幅方向に隣接するように配置されている。変速装置ケース50の前側部分50cよりも後側に位置する部分50dは、前後方向において、クランクケース32よりも後側に位置している。後側部分50dは、後輪18の左側に位置している。
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。
図3に示すように、エンジンユニット20には、オイル溜まり99が設けられている。オイル溜まり99には、オイルが溜められている。オイル溜まり99に溜められたオイルは、エンジン30の各摺動部と、有段式自動変速装置31の各ギア対83~86,90,91,96と、第2,第4のクラッチ70,66とに供給される。
次に有段式自動変速装置31の動作について、図8~図11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8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9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10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に示す油圧切り替えバルブ143が駆動され、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。
上記実施形態では、カバー部材11の内部空間が収納スペース11aとして利用される例について説明した。但し、カバー部材11の内部空間は、収納スペース以外の空間として利用されていてもよい。カバー部材11の内部空間は、例えば電装部品などの配置スペース、燃料タンクなどとして利用されていてもよい。
Claims (6)
- 車体フレームと、
前記車体フレームに揺動可能に懸架され、エンジンと、有段式自動変速装置とを有するエンジンユニットと、
前記エンジンユニットによって駆動される駆動輪と、
少なくとも一部が前記エンジンユニットの上方に位置するように前記車体フレームに取り付けられたシートと、
前記車体フレームに取り付けられ、少なくとも一部が前記シートと前記エンジンユニットとの間に位置する内部空間を区画形成するカバー部材と、
を備え、
前記エンジンは、
クランク室が内部に区画形成されたクランクケースと、
前記クランク室に収納されたクランク軸と、
前記クランクケースに接続され、中心軸が前記クランクケースから前側に向かって斜め上方に延びるシリンダが形成されたシリンダボディと、
を有し、
前記有段式自動変速装置は、
前側部分が前記クランクケースと車幅方向に隣接するように配置され、内部に変速装置室が区画形成された変速装置ケースと、
前記変速装置室内に配置され、前記クランクケースの回転が伝達される入力軸と、
前記変速装置室内において前記入力軸よりも後側に配置され、前記駆動輪が取り付けられた出力軸と、
前記変速装置室内に配置され、前記入力軸側の回転を前記出力軸側に伝達し、相互に減速比が異なる複数組のギア対と、
を有し、
前記クランク室の底部と、前記変速装置ケースの前記前側部分に位置する前記変速装置室の部分の底部とのそれぞれには、前記エンジンの各摺動部と前記複数組のギア対とに供給されるオイルが溜められたオイル溜まりが形成されており、
前記クランクケースと前記変速装置ケースとには、前記クランクケースに形成されたオイル溜まりと、前記変速装置ケースに形成されたオイル溜まりとを相互に連通させる連通経路が形成されており、
前記変速装置室の前記オイル溜まりが形成された部分の底面は、前記変速装置室の前記オイル溜まりよりも後側の部分の底面よりも下側に位置している自動二輪車。 - 請求項1に記載された自動二輪車において、
前記エンジンの各摺動部と、前記複数組のギア対との両方に前記オイル溜まりに溜められたオイルを供給するオイルポンプをさらに備える自動二輪車。 - 請求項1に記載された自動二輪車において、
前記クランクケースは、前記車体フレームに対して揺動可能に取り付けられた取り付け部を有する自動二輪車。 - 請求項1に記載された自動二輪車において、
前記クランクケースと前記変速装置ケースとのうちの少なくとも一方は、前記クランク軸の軸心よりも前側に設けられており、前記車体フレームに対して揺動可能に取り付けられた取り付け部を有する自動二輪車。 - 請求項4に記載された自動二輪車において、
前記取り付け部は、前記シリンダボディよりも下側に設けられている自動二輪車。 - 請求項1に記載された自動二輪車において、
上記有段式自動変速装置は、
前記入力軸と前記出力軸との間の動力伝達経路上に配置された中間軸と、
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クラッチと、
をさらに有し、
前記複数組のギア対は、
前記クラッチが切断状態にあるときに前記中間軸の回転を前記出力軸側へと伝達する第1のギア対と、
前記第1のギア対とは異なる減速比を有し、前記クラッチが接続状態にあるときに前記中間軸の回転を前記出力軸側へと伝達する第2のギア対と、
を含み、
前記中間軸の軸心は、前記入力軸の軸心と前記出力軸の軸心とを含む平面よりも上側または下側に位置している自動二輪車。
Priority Applications (8)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
MX2011001471A MX2011001471A (es) | 2008-08-08 | 2009-01-16 | Motocicleta. |
ES09804649T ES2390026T3 (es) | 2008-08-08 | 2009-01-16 | Vehículo a motor de dos ruedas |
EP09804649A EP2309152B1 (en) | 2008-08-08 | 2009-01-16 | Two-wheeled motor vehicle |
BRPI0916313A BRPI0916313A2 (pt) | 2008-08-08 | 2009-01-16 | motocicleta |
AP2011005579A AP2899A (en) | 2008-08-08 | 2009-01-16 | Two-wheeled motor vehicle |
CN200980130594.5A CN102112781B (zh) | 2008-08-08 | 2009-01-16 | 机动二轮车 |
US13/057,803 US8720632B2 (en) | 2008-08-08 | 2009-01-16 | Two-wheeled motor vehicle |
TW098113896A TWI375633B (en) | 2008-08-08 | 2009-04-27 | Motorcycle |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2008-204926 | 2008-08-08 | ||
JP2008204926 | 2008-08-08 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2010016162A1 true WO2010016162A1 (ja) | 2010-02-11 |
Family
ID=41663391
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2009/000140 WO2010016162A1 (ja) | 2008-08-08 | 2009-01-16 | 自動二輪車 |
Country Status (10)
Country | Link |
---|---|
US (1) | US8720632B2 (ja) |
EP (1) | EP2309152B1 (ja) |
CN (1) | CN102112781B (ja) |
AP (1) | AP2899A (ja) |
BR (1) | BRPI0916313A2 (ja) |
CO (1) | CO6300880A2 (ja) |
ES (1) | ES2390026T3 (ja) |
MX (1) | MX2011001471A (ja) |
TW (1) | TWI375633B (ja) |
WO (1) | WO2010016162A1 (ja) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
ITUB20152778A1 (it) * | 2015-08-03 | 2017-02-03 | Piaggio & C Spa | Cambio sincrono a tre velocita |
IT201600122091A1 (it) * | 2016-12-01 | 2018-06-01 | Piaggio & C Spa | Trasmissione sincrona a elevato rendimento |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5722448A (en) * | 1980-07-16 | 1982-02-05 | Suzuki Motor Co Ltd | Automatic three-speed gear |
JPS6223349Y2 (ja) * | 1982-01-20 | 1987-06-13 | ||
JPH04282054A (ja) * | 1991-03-07 | 1992-10-07 | Suzuki Motor Corp | 自動二輪車のエンジン潤滑回路 |
JPH10299873A (ja) | 1997-04-30 | 1998-11-13 | Suzuki Motor Corp | スクーター型車両のvベルト自動変速機冷却装置 |
JP2003278893A (ja) * | 2002-03-25 | 2003-10-02 | Kawasaki Heavy Ind Ltd | 車輌用エンジン |
JP2003306191A (ja) * | 2002-04-16 | 2003-10-28 | Suzuki Motor Corp | 自動二輪車のパワーユニット |
JP2007285372A (ja) * | 2006-04-14 | 2007-11-01 | Honda Motor Co Ltd | 平行軸式変速機 |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2679166A (en) * | 1951-06-02 | 1954-05-25 | Kreis Fritz | Automatically operating change speed gear, particularly for motorcycles |
US2671349A (en) * | 1951-06-02 | 1954-03-09 | Kreis Fritz | Automatically operating change-speed gear |
GB2081823B (en) * | 1980-08-08 | 1984-04-26 | Suzuki Motor Co | Automatic transmissions |
JPS58118481A (ja) * | 1982-01-09 | 1983-07-14 | 本田技研工業株式会社 | 自動二輪車のスイング式パワ−ユニツト |
JPS5996414A (ja) * | 1982-11-24 | 1984-06-02 | Yamaha Motor Co Ltd | 自動二輪車等の車両におけるエンジンユニツト |
ITTO20050666A1 (it) * | 2004-09-29 | 2006-03-30 | Honda Motor Co Ltd | Motociclo |
JP4556611B2 (ja) * | 2004-10-19 | 2010-10-06 | スズキ株式会社 | 自動二輪車のパワーユニット |
MX2011001469A (es) * | 2008-08-08 | 2011-03-25 | Yamaha Motor Co Ltd | 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 |
-
2009
- 2009-01-16 WO PCT/JP2009/000140 patent/WO2010016162A1/ja active Application Filing
- 2009-01-16 AP AP2011005579A patent/AP2899A/xx active
- 2009-01-16 MX MX2011001471A patent/MX2011001471A/es active IP Right Grant
- 2009-01-16 EP EP09804649A patent/EP2309152B1/en not_active Not-in-force
- 2009-01-16 ES ES09804649T patent/ES2390026T3/es active Active
- 2009-01-16 BR BRPI0916313A patent/BRPI0916313A2/pt not_active Application Discontinuation
- 2009-01-16 US US13/057,803 patent/US8720632B2/en not_active Expired - Fee Related
- 2009-01-16 CN CN200980130594.5A patent/CN102112781B/zh not_active Expired - Fee Related
- 2009-04-27 TW TW098113896A patent/TWI375633B/zh not_active IP Right Cessation
-
2011
- 2011-02-08 CO CO11014401A patent/CO6300880A2/es active IP Right Grant
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5722448A (en) * | 1980-07-16 | 1982-02-05 | Suzuki Motor Co Ltd | Automatic three-speed gear |
JPS6223349Y2 (ja) * | 1982-01-20 | 1987-06-13 | ||
JPH04282054A (ja) * | 1991-03-07 | 1992-10-07 | Suzuki Motor Corp | 自動二輪車のエンジン潤滑回路 |
JPH10299873A (ja) | 1997-04-30 | 1998-11-13 | Suzuki Motor Corp | スクーター型車両のvベルト自動変速機冷却装置 |
JP2003278893A (ja) * | 2002-03-25 | 2003-10-02 | Kawasaki Heavy Ind Ltd | 車輌用エンジン |
JP2003306191A (ja) * | 2002-04-16 | 2003-10-28 | Suzuki Motor Corp | 自動二輪車のパワーユニット |
JP2007285372A (ja) * | 2006-04-14 | 2007-11-01 | Honda Motor Co Ltd | 平行軸式変速機 |
Non-Patent Citations (1)
Title |
---|
See also references of EP2309152A4 |
Also Published As
Publication number | Publication date |
---|---|
US20110127099A1 (en) | 2011-06-02 |
ES2390026T3 (es) | 2012-11-06 |
EP2309152A1 (en) | 2011-04-13 |
TW201008822A (en) | 2010-03-01 |
MX2011001471A (es) | 2011-03-25 |
US8720632B2 (en) | 2014-05-13 |
CN102112781B (zh) | 2014-09-03 |
BRPI0916313A2 (pt) | 2015-12-15 |
CN102112781A (zh) | 2011-06-29 |
TWI375633B (en) | 2012-11-01 |
AP2011005579A0 (en) | 2011-02-28 |
AP2899A (en) | 2014-05-31 |
EP2309152B1 (en) | 2012-06-20 |
CO6300880A2 (es) | 2011-07-21 |
EP2309152A4 (en) | 2011-08-17 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP2013217473A (ja) | ギアボックスおよびそれを備えた鞍乗型車両 | |
JP5525288B2 (ja) | 車両用エンジン | |
JP4331785B2 (ja) | パワーユニット及びそれを備えたモーターサイクル | |
WO2010016162A1 (ja) | 自動二輪車 | |
JP4335960B2 (ja) | 有段式自動変速装置及びそれを備えた車両 | |
JP6223163B2 (ja) | 車輌用エンジン及び該エンジンを備えた自動二輪車 | |
EP2309151B1 (en) | Stepwise automatic transmission for saddle riding type vehicle, power unit equipped with the same, and saddle riding type vehicle equipped with the same | |
JP4319693B2 (ja) | 有段式自動変速装置、それを備えたパワーユニット及び車両 | |
JP2009068700A (ja) | 有段式自動変速装置及びそれを備えた車両 | |
JP2008075713A (ja) | 車輌用エンジン | |
JP4327230B2 (ja) | 有段式自動変速装置及びそれを備えたモーターサイクル | |
JP2010007847A (ja) | エンジンのオイル供給構造 | |
JP4327229B2 (ja) | 有段式自動変速装置、それを備えたパワーユニット、及びそれを備えたモーターサイクル | |
JP2009068699A (ja) | 有段式自動変速装置及びそれを備えた車両 | |
JP2016053326A (ja) | 多気筒エンジン | |
JP5898775B2 (ja) | 過給機付きエンジン | |
JP4319694B2 (ja) | 鞍乗型車両用の有段式自動変速装置、それを備えたパワーユニット及びそれを備えた鞍乗型車両 | |
JP6230895B2 (ja) | 自動二輪車 | |
JP6160335B2 (ja) | 並列多気筒エンジン | |
JP2007278107A (ja) | 鞍乗型車両 | |
JP2011179483A (ja) | 多気筒エンジン |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
WWE | Wipo information: entry into national phase |
Ref document number: 200980130594.5 Country of ref document: CN |
|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 09804649 Country of ref document: EP Kind code of ref document: A1 |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2009804649 Country of ref document: EP |
|
WWE | Wipo information: entry into national phase |
Ref document number: 227/KOLNP/2011 Country of ref document: IN |
|
WWE | Wipo information: entry into national phase |
Ref document number: 13057803 Country of ref document: US |
|
WWE | Wipo information: entry into national phase |
Ref document number: 11014401 Country of ref document: CO Ref document number: MX/A/2011/001471 Country of ref document: MX |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
ENP | Entry into the national phase |
Ref document number: PI0916313 Country of ref document: BR Kind code of ref document: A2 Effective date: 20110124 |