WO2015156266A1 - 車両用変速装置 - Google Patents
車両用変速装置 Download PDFInfo
- Publication number
- WO2015156266A1 WO2015156266A1 PCT/JP2015/060792 JP2015060792W WO2015156266A1 WO 2015156266 A1 WO2015156266 A1 WO 2015156266A1 JP 2015060792 W JP2015060792 W JP 2015060792W WO 2015156266 A1 WO2015156266 A1 WO 2015156266A1
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- WIPO (PCT)
- Prior art keywords
- transmission
- shaft
- gear
- driving force
- shift
- 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
- F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
- F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
- F16H63/08—Multiple final output mechanisms being moved by a single common final actuating mechanism
- F16H63/20—Multiple final output mechanisms being moved by a single common final actuating mechanism with preselection and subsequent movement of each final output mechanism by movement of the final actuating mechanism in two different ways, e.g. guided by a shift gate
- F16H63/22—Multiple final output mechanisms being moved by a single common final actuating mechanism with preselection and subsequent movement of each final output mechanism by movement of the final actuating mechanism in two different ways, e.g. guided by a shift gate the final output mechanisms being simultaneously moved by the final actuating mechanism
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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
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/04—Combinations of toothed gearings only
- F16H37/042—Combinations of toothed gearings only change gear transmissions in group arrangement
- F16H37/043—Combinations of toothed gearings only change gear transmissions in group arrangement without gears having orbital motion
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
- F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
- F16H63/08—Multiple final output mechanisms being moved by a single common final actuating mechanism
- F16H63/16—Multiple final output mechanisms being moved by a single common final actuating mechanism the final output mechanisms being successively actuated by progressive movement of the final actuating mechanism
- F16H63/18—Multiple final output mechanisms being moved by a single common final actuating mechanism the final output mechanisms being successively actuated by progressive movement of the final actuating mechanism the final actuating mechanism comprising cams
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
- F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
- F16H63/30—Constructional features of the final output mechanisms
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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
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/04—Combinations of toothed gearings only
- F16H37/042—Combinations of toothed gearings only change gear transmissions in group arrangement
- F16H37/043—Combinations of toothed gearings only change gear transmissions in group arrangement without gears having orbital motion
- F16H2037/045—Combinations of toothed gearings only change gear transmissions in group arrangement without gears having orbital motion comprising a separate gearing unit for shifting between high and low ratio range
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
- F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
- F16H63/08—Multiple final output mechanisms being moved by a single common final actuating mechanism
- F16H63/20—Multiple final output mechanisms being moved by a single common final actuating mechanism with preselection and subsequent movement of each final output mechanism by movement of the final actuating mechanism in two different ways, e.g. guided by a shift gate
- F16H2063/202—Multiple final output mechanisms being moved by a single common final actuating mechanism with preselection and subsequent movement of each final output mechanism by movement of the final actuating mechanism in two different ways, e.g. guided by a shift gate using cam plates for selection or shifting, e.g. shift plates with recesses or groves moved by a selector extension
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/006—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eight forward speeds
Definitions
- the present invention relates to a transmission for a vehicle that transmits a driving force from a crankshaft through a plurality of gears.
- An engine mounted on a vehicle such as a motorcycle includes a transmission that transmits a driving force of a crankshaft to a driving wheel via a clutch mechanism.
- a transmission includes a counter shaft (input shaft) and a drive shaft (output shaft) extending in parallel with the vehicle width direction, and a plurality of transmission gears mounted on each shaft, and changes the combination of meshing transmission gears. Shifting with.
- the number of shift stages is often set to six.
- Patent Document 2 in a rough terrain vehicle (for example, a four-wheel buggy), a sub-transmission is used in addition to a normal transmission in order to widen the range of the gear ratio. Yes.
- a normal transmission and a sub-transmission are provided with two drive shafts, and gears that mesh with each drive shaft are provided to perform sub-transmission.
- the present invention has been made in view of the above points, and an object of the present invention is to provide a vehicular transmission that can suppress an increase in the shaft lengths of an input shaft and an output shaft and can increase the number of shift stages. To do.
- the transmission for a vehicle is a transmission that transmits a driving force of a crankshaft from a first transmission to a drive wheel side through a second transmission, and the first transmission is driven from the crankshaft.
- the first and second transmissions are arranged side by side in front and back, and the number of shift stages is set to a plurality.
- the second transmission is provided in addition to the first transmission, and multiple transmissions can be performed in each transmission. Therefore, the length of the input shaft and the output shaft of each transmission in the vehicle width direction can be increased.
- each of the first and second transmissions includes a slide dog, and the slide dog is selectively joined to the first and second transmission gears.
- the second transmission gear can transmit the driving force
- a single shift mechanism is provided at a position adjacent to each of the first and second transmissions.
- the shift mechanism transmits a first driving force.
- both the transmission gears of the first and second transmissions can be switched at the same time, and operability can be improved.
- the shift mechanism includes a single shift cam having a plurality of lead grooves formed on the outer periphery thereof, and the lead cams are displaced by rotating the shift cams.
- the first and second transmission gears to which the slide dogs are joined may be switched. According to this configuration, even if the number of shift stages is increased, the configuration of the shift mechanism can be simplified by a single shift cam in which a plurality of lead grooves are formed.
- the first input shaft is disposed above the first output shaft
- the second output shaft is disposed above the second input shaft
- the first input shaft and the The second output shaft may be arranged side by side. According to this configuration, the two input shafts and the output shafts can be arranged in the front-rear and top-bottom directions, and these shafts can be closely packed to reduce the overall size of the transmission.
- the center position of the crankshaft, the first input shaft, and the second output shaft is substantially the same when viewed in their extending direction. It is good to be arranged. According to this configuration, layout design in the transmission can be easily performed.
- the second transmission is provided in addition to the first transmission, and multiple transmissions can be performed in each transmission, so that the shaft lengths of the input shaft and the output shaft are long. It is possible to increase the number of shift stages while suppressing this.
- FIG. 3 is a simplified cross-sectional view cut along a plane passing through O1, O2, O3, O4, and O5 of FIG. 2.
- FIG. 3 is a simplified cross-sectional view cut along a plane passing through O3, O7, O6, O8, and O4 of FIG. 2. It is an outer diameter expansion
- FIG. 1 is a right side view of a crankcase provided with a vehicle transmission
- FIG. 2 is a conceptual diagram in which a part of the configuration of FIG. 1 is omitted and simplified.
- the front of the vehicle is indicated by an arrow FR
- the rear of the vehicle is indicated by an arrow RE
- the left side of the vehicle is indicated by an arrow L
- the right side of the vehicle is indicated by an arrow R
- the vehicle width direction is indicated by an arrow W.
- a crankshaft 11 is disposed in front of the crankcase 10, and the crankshaft 11 has a rotation shaft disposed in parallel to the vehicle width direction (the direction orthogonal to the plane of FIG. 1). .
- a transmission 20 is disposed in the rear side of the crankcase 10. As shown also in FIG. 2, the transmission 20 is adjacent to the first transmission 21 disposed behind the crankshaft 11, the rear of the first transmission 21, and arranged side by side with the first transmission 21.
- the second transmission 22 is disposed, and a single shift mechanism 23 is disposed at an adjacent position below the first and second transmissions 21 and 22.
- FIG. 3 is a simplified cross-sectional view cut along a plane passing through points O1, O2, O3, O4, and O5 in FIG.
- a primary drive gear 12 is integrally provided at one end (right end) of the crankshaft 11 so as to rotate integrally.
- the first transmission 21 includes a first counter shaft (first input shaft) 25 and a first drive shaft (first output shaft) 26.
- the second transmission 22 includes a second counter shaft (second input shaft) 27 and a second drive shaft (second output shaft) 28.
- Each of the shafts 25 to 28 is arranged in parallel to the vehicle width direction similarly to the crankshaft 11, and both ends thereof are rotatably supported by the crankcase 10 (see FIG. 1) via bearings 30.
- points O1 to O5 indicate the axial center positions of the crankshaft 11, the first counter shaft 25, the first drive shaft 26, the second counter shaft 27, and the second drive shaft 28.
- the positions of the centers O1, O2, and O5 are arranged along substantially the same straight line indicated by a two-dot chain line in FIG. Thereby, simplification of the layout of these shafts 11, 25, 28 can be achieved.
- a first counter shaft 25 is disposed above the first drive shaft 26, and a second drive shaft 28 is disposed above the second counter shaft 27.
- the first counter shaft 25 and the second drive shaft 28 are arranged side by side.
- the four shafts 25 to 28 are arranged densely in the front-rear direction and the up-down direction, and the transmission 20 can be reduced in size in the same direction.
- a primary driven gear 32 that meshes with the primary drive gear 12 is rotatably provided on the first counter shaft 25.
- An input-side outer case (clutch housing) 34 of the clutch mechanism 33 is fixed to the primary driven gear 32 so as to rotate together.
- an output side inner hub 35 of the clutch mechanism 33 is fixed to one end side of the first counter shaft 25.
- the outer case 34 and the inner hub 35 are connected to each other through a plurality of friction plates so as to be intermittently operated, whereby the driving force from the crankshaft 11 is transmitted to the first countershaft 25 via the clutch mechanism 33. Is done.
- the first transmission 21 further includes four first input transmission gears (first transmission gears) provided on the first counter shaft 25 and having different numbers of teeth.
- the first input side transmission gears are, in order from the right, a first input side first speed gear 37a, a first input side third speed gear 37c, a first input side fourth speed gear 37d, and a first input side second speed gear 37b.
- the meshing pitch circle diameter increases in the order of the first input side first speed gear 37a, the first input side second speed gear 37b, the first input side third speed gear 37c, and the first input side fourth speed gear 37d.
- These gears 37a to 37d are spline-fitted or integrally formed with the first counter shaft 25, rotate integrally with the first counter shaft 25, and are fixed so as not to move in the axial direction.
- the first transmission 21 further includes four first output side transmission gears (first transmission gears) provided on the first drive shaft 26 with different numbers of teeth.
- the first output side transmission gears are, in order from the right, a first output side first speed gear 38a, a first output side third speed gear 38c, a first output side fourth speed gear 38d, and a first output side second speed gear 38b. . Further, the meshing pitch circle diameter becomes smaller in the order of the first output side first speed gear 38a, the first output side second speed gear 38b, the first output side third speed gear 38c, and the first output side fourth speed gear 38d.
- These gears 38a to 38d are rotatably provided to the first drive shaft 26 so as to be idle, and are mounted so as not to move in the axial direction.
- the first output side gears 38a to 38d are always meshed with the first input side gears 37a to 37d.
- the reduction drive gear 40 is fixed to one end (left end) side of the first drive shaft 26 so as to rotate integrally.
- a reduction driven gear 41 is fixed to one end (left end) side of the second countershaft 27 so as to rotate integrally.
- the reduction drive gear 40 and the reduction driven gear 41 mesh with each other, and the driving force of the first drive shaft 26 is transmitted to the second countershaft 27 via these gears 40 and 41.
- the reduction drive gear 40 and the reduction driven gear 41 constitute a transmission mechanism.
- the second transmission 22 further includes two second input side transmission gears (second transmission gears) provided on the second countershaft 27 and having different numbers of teeth.
- the second input side transmission gears are, in order from the right, a second input side first speed gear 43a and a second input side second speed gear 43b. These gears 43a and 43b are rotatably provided to the second countershaft 27 so as to be able to idle, and are mounted so as not to move in the axial direction.
- the second transmission 22 further includes two second output side transmission gears (second transmission gears) provided on the second drive shaft 28 with different numbers of teeth.
- the second output side transmission gears are, in order from the right, a second output side first speed gear 44a and a second output side second speed gear 44b.
- These gears 44a and 44b are spline-fitted or integrally formed with the second drive shaft 28, rotate integrally with the second drive shaft 28, and are fixed so as not to move in the axial direction.
- the gears 44a and 44b on the second output side are always meshed with the gears 43a and 43b on the second input side.
- a drive sprocket 46 is provided at one end (left end) of the second drive shaft 28.
- the drive sprocket 46 is connected to a driven sprocket (not shown) provided on a drive wheel (not shown) via a drive chain 47, and the drive force of the second drive shaft 28 is driven to the drive wheel side by this chain drive. To communicate.
- first drive shaft 26 is provided with first and second slide dogs 51 and 52
- the second countershaft 27 is provided with a third slide dog 53.
- the first slide dog 51 is disposed between the first output side first speed gear 38a and the first output side third speed gear 38c
- the second slide dog 52 includes the first output side fourth speed gear 38d, It is arranged between the first output side second gear 38b.
- the first and second slide dogs 51 and 52 are spline-fitted to the first drive shaft 26, rotate integrally with the first drive shaft 26, and are mounted so as to be movable in the axial direction.
- a dog clutch 55 is integrally formed on the side surface of the first slide dog 51 and the side surfaces of the first output side first speed gear 38a and the first output side third speed gear 38c by a concave portion or a convex portion.
- the dog clutch 56 similar to the above is integrally formed on the side surface of the second slide dog 52 and the side surfaces of the first output side fourth speed gear 38d and the first output side second speed gear 38b.
- the gears 38a to 38d meshed with the dog clutches 55 and 56 of the first and second slide dogs 51 and 52, and any of the first input side transmission gears 37a to 37d meshed with the gears 38a to 38d.
- the driving force from the first counter shaft 25 is transmitted.
- a third slide dog 53 is provided between the second input side first speed gear 43a and the second input side second speed gear 43b of the second countershaft 27.
- the third slide dog 53 is spline-fitted to the second countershaft 27, is rotated integrally with the second countershaft 27, and is mounted so as to be movable in the axial direction.
- a dog clutch 57 similar to the above is integrally formed on the side surface of the third slide dog 53 and the side surfaces of the second input side first speed gear 43a and the second input side second speed gear 43b.
- the second drive shaft 28 is connected to either the gear 43a, 43b meshed with the dog clutch 57 of the third slide dog 53 and the second output side transmission gear 44a, 44b meshed with the gear 43a, 43b. Transmits driving force.
- the shift mechanism 23 includes a shift pedal shaft 60, a shift drive plate 61, a shift cam 62, and a shift pedal arm (not shown). Further, the shift mechanism 23 includes first to third shift forks 63 to 65 and first and second shift shafts 67 and 68 as shown in FIGS. 1 and 2, points O6 to O8 indicate the axial center positions of the first shift shaft 67, the shift cam 62, and the second shift shaft 68.
- the first and second shift shafts 67 and 68 are arranged in parallel to the vehicle width direction.
- the first shift shaft 67 is provided at a position below the first drive shaft 26, and the second shift shaft 68 is provided at a position below the second counter shaft 27.
- the first and second shift forks 63 and 64 are attached to the first shift shaft 67 so as to be slidable in the axial direction
- the third shift fork 65 is attached to the second shift shaft 68 so as to be slidable in the axial direction.
- the tips of the first to third shift forks 63 to 65 (not shown in FIG. 4) have a bifurcated shape and engage with the first to third slide dogs 51 to 53.
- the first to third shift forks 63 to 65 are provided with first to third pins 63a, 64a and 65a at the base, and these pins 63a, 64a and 65a are first to third leads (to be described later) of the shift cam 62, respectively.
- the grooves 71 to 73 are received.
- the shift cam 62 is rotationally operated stepwise via a shift pedal shaft 60 and a shift drive plate 61 in conjunction with a shift operation of a shift pedal arm (not shown).
- the shift cam 62 is disposed in parallel with the shafts 26 and 27 in the vicinity of the lower side of the first drive shaft 26 and the second counter shaft 27 and is pivotally supported.
- the shift cam 62 is a cylindrical cam cast, for example, in a hollow shape, and first to third lead grooves 71 to 73 are formed on the outer peripheral surface as three lead grooves.
- the first to third lead grooves 71 to 73 extend in the circumferential direction of the shift cam 62 and are spaced apart in the axial direction of the shift cam 62.
- a first pin 63a is received in the first lead groove 71
- a second pin 64a is received in the second lead groove 72
- a third pin 65a is slidably received in the third lead groove 73. .
- Fig. 5 is a developed view of the shift cam.
- the numbers on the surface of the shift cam 62 in FIG. 5 indicate the positions of the pins 63a, 64a, 65a at the gear positions of the numbers.
- the number in the third lead groove 73 is the angle ⁇ in FIG. 2 with respect to the number in the first and second lead grooves 71 and 72 (gear position).
- the position corresponding to is displaced downward.
- the neutral (N) is positioned lower than the first speed.
- Each of the lead grooves 71 to 73 extends between the gear positions in parallel to the circumferential direction of the shift cam 62, and the left and right positions of the pins 63a, 64a, and 65a change even if the shift cam 62 is rotated to change speed. Absent.
- each lead groove 71 ⁇ is positioned at a position where the pins 63a, 64a, 65a are received. The left and right positions of 73 are displaced.
- the shift cam 62 by rotating the shift cam 62 by a predetermined rotation amount, the left and right positions of the lead grooves 71 to 73 are displaced, and the first to third shift forks 63 to 65 move in the axial direction (left and right direction).
- the first to third slide docks 51 to 53 engaged with the first to third shift forks 63 to 65 are selectively moved in the axial direction, and the first to third slide docks 51 to 53 are joined.
- Each gear is switched.
- the gears to which the first to third slide docks 51 to 53 are joined are simultaneously switched by the rotation of the shift cam 62.
- the axial position of the pin 63a is neutral, and the first slide dog 51 is the first output side first speed gear. 38a and the first output side third speed gear 38c are not in contact with each other. Therefore, both the first output side first speed gear 38a and the first output side third speed gear 38c are idle with respect to the first drive shaft 26.
- the axial position of the pin 63a is shifted to the right, and the first slide dog 51 is joined to the first output side first speed gear 38a via the dog clutch 55. .
- the driving force is transmitted from the first counter shaft 25 to the first drive shaft 26 via the first input side first speed gear 37a and the first output side first speed gear 38a.
- the axial position of the pin 63a is shifted to the left, and the first slide dog 51 is joined to the first output side third speed gear 38c via the dog clutch 55.
- the driving force is transmitted from the first counter shaft 25 to the first drive shaft 26 via the first input side third gear 37c and the first output side third gear 38c.
- the axial position of the pin 64a is neutral, and the second slide dog 52 is in the first output side fourth speed gear. 38d and the first output side second speed gear 38b are not in contact with each other. Accordingly, both the first output side fourth speed gear 38d and the first output side second speed gear 38b are idle with respect to the first drive shaft 26.
- the axial position of the pin 64a is shifted to the left, and the second slide dog 52 is joined to the first output side second speed gear 38b via the dog clutch 56. .
- the driving force is transmitted from the first counter shaft 25 to the first drive shaft 26 via the first input side second speed gear 37b and the first output side second speed gear 38b.
- the axial position of the pin 64a is shifted to the right, and the second slide dog 52 is joined to the first output side fourth speed gear 38d via the dog clutch 56.
- the driving force is transmitted from the first counter shaft 25 to the first drive shaft 26 via the first input side fourth gear 37d and the first output side fourth gear 38d.
- the axial position of the pin 65a is shifted to the right, and the third slide dog 53 is moved through the dog clutch 57. It is joined to the 2-input side 1st gear 43a. Accordingly, the driving force is transmitted from the second counter shaft 27 to the second drive shaft 28 via the second input side first speed gear 43a and the second output side first speed gear 44a.
- the axial position of the pin 65a is shifted to the left, and the third slide dog 53 is connected to the second input side second speed via the dog clutch 57.
- Joined to the gear 43b Joined to the gear 43b. Accordingly, the driving force is transmitted from the second counter shaft 27 to the second drive shaft 28 via the second input side second speed gear 43b and the second output side second speed gear 44b.
- a shift using each gear is performed by the first to third lead grooves 71 to 73.
- the number of stages is increased every two stages (even to odd)
- the gear for transmitting the driving force is changed and the gear ratio is gradually reduced.
- the first transmission 21 does not change the gear for transmitting the driving force when the number of steps is increased from an odd number to an even number, and when the number of steps is decreased from an even number to an odd number.
- the gear for transmitting the driving force changes, and the odd-numbered stage has a smaller gear ratio than the even-numbered stage.
- the gear ratio of the entire transmission 20 with respect to the gear ratio of the first and second transmissions 21 and 22 is as shown in Table 1 below.
- the gear ratios shown in Table 1 when the number of gears is increased and the gear ratio of the second transmission 22 is increased from B2 to B1, the first and second transmissions 21 are set so that the gear ratio of the entire transmission 20 is reduced. , 22 are respectively set. Accordingly, the gear ratio can be gradually reduced as the number of steps is increased while the transmission device 20 is multistaged from the first to eighth speeds.
- the gear position is the fourth speed
- the first slide dog 51 is in the neutral position by the first lead groove 71
- the second slide dog 52 is in the left position by the second lead groove 72.
- the second slide dog 52 and the first output side second speed gear 38b are joined via the dog clutch 56, and the first output side second speed gear 38b and the first drive shaft 26 rotate together. It becomes.
- the rotation of the first input side second speed gear 37b causes the first output side second speed gear 38b and the first drive shaft 26 to mesh with each other, and the first countershaft is connected via these gears 37b, 38b.
- the driving force is transmitted from 25 to the first drive shaft 26.
- the driving force of the first drive shaft 26 is transmitted to the second countershaft 27 via a reduction drive gear 40 and a reduction driven gear 41 that mesh with each other.
- the third slide dog 53 is located on the left side by the third lead groove 73.
- the third slide dog 53 and the second input side second speed gear 43b are joined via the dog clutch 57, and the second input side second speed gear 43b and the second counter shaft 27 rotate together. It becomes.
- the second output side second speed gear 44b and the second drive shaft 28 which are meshed with the second input side second speed gear 43b rotate, and the second countershaft is rotated via these gears 43b and 44b.
- the driving force is transmitted from 27 to the second drive shaft 28.
- the driving force of the second drive shaft 28 is transmitted to a drive wheel (not shown) such as a rear wheel via a drive sprocket 46 and a drive chain 47.
- the first slide dog 51 When the gear position is changed from the fourth speed to the fifth speed, the first slide dog 51 is positioned to the left by the first lead groove 71, and the second slide dog 52 is set to the neutral position by the second lead groove 72. Accordingly, the connection between the second slide dog 52 and the first output side second gear 38b is released, and the first slide dog 51 and the first output side third gear 38c are switched to be joined. That is, in the first transmission 21, the gear for transmitting the driving force is switched to the first output side third speed gear 38c and the first input side third speed gear 37c, and the first countershaft is connected via these gears 37c, 38c. The driving force is transmitted from 25 to the first drive shaft 26.
- the third slide dog 53 is located on the right side by the third lead groove 73. Accordingly, the joining target of the third slide dog 53 is switched, the joining of the third slide dog 53 and the second input side second speed gear 43b is released, and the third slide dog 53 and the second input side first speed gear are released. 43a is joined. That is, in the second transmission 22, the gear for transmitting the driving force is switched to the second input side first speed gear 43a and the second output side first speed gear 44a, and the second countershaft is connected via these gears 43a and 44a. The driving force is transmitted from 27 to the second drive shaft 28.
- the number of shift stages can be increased as compared with a six-speed transmission having a countershaft and a drive shaft provided with six transmission gears.
- the shaft lengths of the shafts 25 and 27 and the drive shafts 26 and 28 can be shortened.
- the distance between the bearings 30 that support the shafts 25 to 28 can be shortened, and the strength of the shafts 25 to 28 can be prevented from being reduced due to bending deformation or the like.
- the overhang of the clutch mechanism 33 with respect to the engine center in the vehicle width direction and the offset amount of the drive chain 47 and the like can be reduced, and the mass of the transmission 20 can be concentrated on the engine center. As a result, it is possible to improve the exercise performance as a motorcycle.
- a plurality of lead grooves 71 to 73 are formed in a single shift cam 62 so that the plurality of slide dogs 51 to 53 can be displaced simultaneously.
- the transmissions 21 and 22 can be shifted simultaneously.
- the rotational direction of the drive sprocket 46 is the same as that of the conventional structure with one transmission. be able to. As a result, it is possible to eliminate the need to add an extra shaft to change the rotation direction, and this also simplifies the configuration.
- the number of shift stages of the first and second transmissions 21 and 22 may be changed as long as it is plural.
- the position of the neutral (N) in FIG. 5 is not limited, and may be changed between the first speed and the second speed, for example.
- the present invention has an effect that it is possible to increase the number of shift stages while suppressing an increase in the shaft length of the shaft (shaft), and in particular, a speed change provided in an engine of a motorcycle. Useful for equipment.
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Abstract
Description
Claims (5)
- クランクシャフトの駆動力を第1変速機から第2変速機を通じて駆動輪側に伝達する変速装置であって、
前記第1変速機は、前記クランクシャフトからの駆動力が伝達される第1入力軸と、当該第1入力軸の駆動力が第1変速ギヤを介して伝達される第1出力軸とを備え、
前記第2変速機は、前記第1出力軸の駆動力が伝達機構を介して伝達される第2入力軸と、当該第2入力軸の駆動力が第2変速ギヤを介して伝達されて前記駆動輪側へと伝達する第2出力軸とを備え、
前記第1及び第2変速機は、前後に並んで配置され、且つ、それぞれの変速段数が複数に設定されていることを特徴とする車両用変速装置。 - 前記第1及び第2変速機は、スライドドッグをそれぞれ備え、当該スライドドッグは、前記第1及び第2変速ギヤに選択的に接合して当該接合した第1及び第2変速ギヤによって前記駆動力を伝達可能とし、
前記第1及び第2変速機にそれぞれ隣接する位置には単一のシフト機構が設けられ、このシフト機構は、駆動力を伝達する第1及び第2変速ギヤを同時に切り替え可能に設けられていることを特徴とする請求項1に記載の車両用変速装置。 - 前記シフト機構は、外周に複数のリード溝が形成された単一のシフトカムを含み、当該シフトカムを回動することで各リード溝を変位し、この変位によって前記各スライドドッグが接合する前記第1及び第2変速ギヤを切り替えることを特徴とする請求項2に記載の車両用変速装置。
- 前記第1出力軸の上方に前記第1入力軸が配置され、前記第2入力軸の上方に前記第2出力軸が配置され、前記第1入力軸と前記第2出力軸とは前後に並んで配置されていることを特徴とする請求項2又は請求項3に記載の車両用変速装置。
- 前記クランクシャフトと、前記第1入力軸と、前記第2出力軸とは、それらの延在方向で見たときに、各中心位置が略同一直線に沿って配置されていることを特徴とする請求項1に記載の車両用変速装置。
Priority Applications (2)
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US14/774,699 US9915344B2 (en) | 2014-04-10 | 2015-04-07 | Vehicle transmission device |
DE112015000053.4T DE112015000053B4 (de) | 2014-04-10 | 2015-04-07 | Fahrzeug-Getriebevorrichtung |
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JP2014-081047 | 2014-04-10 | ||
JP2014081047A JP6331620B2 (ja) | 2014-04-10 | 2014-04-10 | 車両用変速装置 |
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WO2015156266A1 true WO2015156266A1 (ja) | 2015-10-15 |
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PCT/JP2015/060792 WO2015156266A1 (ja) | 2014-04-10 | 2015-04-07 | 車両用変速装置 |
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US (1) | US9915344B2 (ja) |
JP (1) | JP6331620B2 (ja) |
DE (1) | DE112015000053B4 (ja) |
WO (1) | WO2015156266A1 (ja) |
Families Citing this family (2)
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JP6459419B2 (ja) * | 2014-11-14 | 2019-01-30 | スズキ株式会社 | 車両用変速装置 |
JP6668127B2 (ja) * | 2016-03-18 | 2020-03-18 | 本田技研工業株式会社 | 車両用変速機構造 |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS612953A (ja) * | 1984-06-15 | 1986-01-08 | Aisin Seiki Co Ltd | 変速機の操作機構 |
JPH0419947U (ja) * | 1990-06-11 | 1992-02-19 | ||
JPH081251B2 (ja) * | 1985-07-19 | 1996-01-10 | ヤマハ発動機株式会社 | 鞍乗型車輛の変速装置 |
JP2001132839A (ja) * | 1999-11-04 | 2001-05-18 | Kubota Corp | 農用トラクタの走行変速装置 |
JP2009156375A (ja) * | 2007-12-27 | 2009-07-16 | Honda Motor Co Ltd | ツインクラッチ式変速装置 |
Family Cites Families (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5823279B2 (ja) * | 1979-09-25 | 1983-05-13 | 本田技研工業株式会社 | 自動二輪車における動力伝達装置 |
JPH0730815B2 (ja) * | 1985-02-18 | 1995-04-10 | スズキ株式会社 | 副変速機 |
GB2358049B (en) * | 1999-11-04 | 2001-12-19 | Kubota Kk | Tractor transmission |
DE10330157A1 (de) * | 2003-07-04 | 2005-02-03 | Zf Friedrichshafen Ag | Lastschaltgetriebe für Baumaschinen, insbesondere für Baggerlader und Telehandler |
JP4501405B2 (ja) * | 2003-10-22 | 2010-07-14 | スズキ株式会社 | 車両用変速装置 |
WO2006055968A2 (en) * | 2004-11-22 | 2006-05-26 | Eaton Corporation | Transmission auxiliary unit shifter inhibitor |
DE102005030987A1 (de) * | 2005-07-02 | 2007-01-18 | Daimlerchrysler Ag | Antriebstrang eines Kraftfahrzeugs |
US8601892B2 (en) * | 2010-01-12 | 2013-12-10 | Borgwarner Inc. | DCT transmission utilizing a two axis chain |
US8720291B2 (en) * | 2010-07-23 | 2014-05-13 | Samir MOUFAWAD | Automatic multi-speed gear system |
JP5087162B1 (ja) * | 2011-08-30 | 2012-11-28 | 株式会社小松製作所 | 作業車両用トランスミッション |
DE102012213667A1 (de) * | 2012-08-02 | 2014-02-06 | Zf Friedrichshafen Ag | Übersetzungsstufe eines Stufengetriebes, sowie Stufengetriebe |
JP6106148B2 (ja) | 2013-11-27 | 2017-03-29 | 日東電工株式会社 | 導電性粘着テープ、電子部材及び粘着剤 |
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2014
- 2014-04-10 JP JP2014081047A patent/JP6331620B2/ja active Active
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2015
- 2015-04-07 WO PCT/JP2015/060792 patent/WO2015156266A1/ja active Application Filing
- 2015-04-07 US US14/774,699 patent/US9915344B2/en active Active
- 2015-04-07 DE DE112015000053.4T patent/DE112015000053B4/de active Active
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS612953A (ja) * | 1984-06-15 | 1986-01-08 | Aisin Seiki Co Ltd | 変速機の操作機構 |
JPH081251B2 (ja) * | 1985-07-19 | 1996-01-10 | ヤマハ発動機株式会社 | 鞍乗型車輛の変速装置 |
JPH0419947U (ja) * | 1990-06-11 | 1992-02-19 | ||
JP2001132839A (ja) * | 1999-11-04 | 2001-05-18 | Kubota Corp | 農用トラクタの走行変速装置 |
JP2009156375A (ja) * | 2007-12-27 | 2009-07-16 | Honda Motor Co Ltd | ツインクラッチ式変速装置 |
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DE112015000053T5 (de) | 2016-01-14 |
JP2015200397A (ja) | 2015-11-12 |
US20160123464A1 (en) | 2016-05-05 |
DE112015000053B4 (de) | 2020-03-26 |
JP6331620B2 (ja) | 2018-05-30 |
US9915344B2 (en) | 2018-03-13 |
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