WO2014025130A1 - 다단 변속기 - Google Patents
다단 변속기 Download PDFInfo
- Publication number
- WO2014025130A1 WO2014025130A1 PCT/KR2013/004823 KR2013004823W WO2014025130A1 WO 2014025130 A1 WO2014025130 A1 WO 2014025130A1 KR 2013004823 W KR2013004823 W KR 2013004823W WO 2014025130 A1 WO2014025130 A1 WO 2014025130A1
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- WIPO (PCT)
- Prior art keywords
- speed
- ring
- pole
- planetary gear
- shaft
- Prior art date
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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
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/30—Chain-wheels
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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
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62M—RIDER PROPULSION OF WHEELED VEHICLES OR SLEDGES; POWERED PROPULSION OF SLEDGES OR SINGLE-TRACK CYCLES; TRANSMISSIONS SPECIALLY ADAPTED FOR SUCH VEHICLES
- B62M11/00—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels
- B62M11/04—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio
- B62M11/14—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio with planetary gears
- B62M11/16—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio with planetary gears built in, or adjacent to, the ground-wheel hub
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62M—RIDER PROPULSION OF WHEELED VEHICLES OR SLEDGES; POWERED PROPULSION OF SLEDGES OR SINGLE-TRACK CYCLES; TRANSMISSIONS SPECIALLY ADAPTED FOR SUCH VEHICLES
- B62M9/00—Transmissions characterised by use of an endless chain, belt, or the like
- B62M9/02—Transmissions characterised by use of an endless chain, belt, or the like of unchangeable ratio
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using 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
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/68—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings
- F16H61/684—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings without interruption of drive
- F16H61/686—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings without interruption of drive with orbital gears
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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
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62M—RIDER PROPULSION OF WHEELED VEHICLES OR SLEDGES; POWERED PROPULSION OF SLEDGES OR SINGLE-TRACK CYCLES; TRANSMISSIONS SPECIALLY ADAPTED FOR SUCH VEHICLES
- B62M11/00—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels
- B62M11/04—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio
- B62M11/14—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio with planetary gears
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62M—RIDER PROPULSION OF WHEELED VEHICLES OR SLEDGES; POWERED PROPULSION OF SLEDGES OR SINGLE-TRACK CYCLES; TRANSMISSIONS SPECIALLY ADAPTED FOR SUCH VEHICLES
- B62M11/00—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels
- B62M11/04—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio
- B62M11/14—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio with planetary gears
- B62M11/18—Transmissions characterised by the use of interengaging toothed wheels or frictionally-engaging wheels of changeable ratio with planetary gears with a plurality of planetary gear units
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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
- F16H2200/0078—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratio comprising twelve or more forward speeds
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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
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital gears
-
- 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
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2079—Transmissions using gears with orbital motion using freewheel type mechanisms, e.g. freewheel clutches
- F16H2200/2087—Transmissions using gears with orbital motion using freewheel type mechanisms, e.g. freewheel clutches three freewheel mechanisms
Definitions
- the present invention relates to a multi-stage transmission, in particular, to implement a compact transmission in more multi-stage by using a planetary gear set, and smooth for both the forward operation according to the acceleration operation as well as the reverse operation according to the deceleration operation using the forced return means.
- the present invention relates to a device capable of improving the merchandise of a product and maximizing user convenience.
- a wheel In general, a wheel is provided, a bicycle, a wheelchair, a cart, and the like, which receive a manpower or travel using various driving power such as electric power, are provided with a transmission for shifting the driving speed.
- Such a transmission can be shifted in multiple stages from a high speed to a low speed according to a rider or a user's operation, so that the required torque or speed can be obtained according to the driving environment.
- a planetary gear set composed of a sun gear, a planetary gear, a ring gear, and a carrier is provided in the hub shell to prevent the gears from being exposed to the outside while changing the speed in multiple stages through a compact configuration. to be.
- the conventional multi-stage transmission using the planetary gear set has fewer shift stages than the complicated structure, and in particular, a smooth shift is not performed because the pawls that engage the inner circumferential surface of the sun gear to restrict rotation of the sun gear are not released. There was a technical problem that it was not working.
- the present invention is to solve the above problems, it is possible to compactly configure the multi-stage transmission using the planetary gear set to improve the productability of the product, using the forced return means of the forward operation of the acceleration operation as well as deceleration It is to provide a multi-stage transmission to maximize the user's ease of use by making a smooth shift even in the reverse operation according to the operation.
- the present invention includes a shaft fixed at both ends and a hub shell rotatably positioned on the outer circumference of the shaft to output a sprocket and a rotational force to receive a rotational force;
- a transmission part including a planetary gear set and a one-way clutch including a sun gear, a planetary gear, a carrier, and a ring gear provided inside the hub shell, and shifting the rotational force input to the sprocket to output the hub shell;
- In the multi-stage transmission including a control unit for controlling the shift by controlling the pole provided on the shaft in accordance with the operation of the shift lever to selectively limit the rotation of the sun gear;
- By shifting the drive pole clutch in the axial direction of the shaft according to the rotation operation of the shift lever a shift is made by selectively transmitting rotational force through a drive pole between a rotating driver and the non-rotating drive pole clutch. Is achieved.
- the first forced return means for selectively controlling the pawl in the engaged state to the forced release state; It is preferable that the second forced return means further comprises a drive pawl clutch and a rotation limiting ring to control the drive pawl in a forced release state.
- the control unit controls the poles in such a way that one or more poles are stacked and rotated integrally in the axial direction of the shaft to selectively control one or more poles in an engaged state or a released state to shift gears. It is most desirable to control.
- the present invention as described above can be configured in a compact gear by using a planetary gear set to improve the productability of the product, by using the forced return means for the forward operation of the acceleration operation as well as the reverse operation of the deceleration operation It is an invention that can maximize the ease of use of the user by making a smooth shift even.
- FIG. 1 is a perspective view showing a multi-stage transmission of the present invention
- FIG. 2 is a front view showing a multi-stage transmission of the present invention
- FIG. 3 is a partially cutaway perspective view illustrating a multistage transmission of the present invention.
- FIG. 4 is a front sectional view showing a multistage transmission of the present invention.
- FIG. 5 is an exploded perspective view illustrating the hub shell of the multi-stage transmission of the present invention.
- FIG. 6 is an exploded perspective view illustrating a third speed planetary gear set of the multi-stage transmission of the present invention.
- FIG. 7 is an exploded perspective view illustrating a second speed planetary gear set of the multi-stage transmission of the present invention.
- FIG. 8 is an exploded perspective view illustrating a sprocket of the multistage transmission of the present invention.
- FIG. 9 is an exploded perspective view illustrating an exploded driver of the multi-stage transmission of the present invention.
- FIG. 10 is an exploded perspective view illustrating an exploded drive pole clutch of the multi-stage transmission of the present invention.
- FIG. 11 is an exploded perspective view illustrating a first speed planetary gear set of the multi-stage transmission of the present invention.
- FIG. 12 is an exploded perspective view illustrating a pole of the multistage transmission of the present invention.
- FIG. 13 is a perspective view showing a control unit of the multi-stage transmission of the present invention.
- Fig. 14 is a view showing the engaged state of the drive poles in the multi-stage transmission of the present invention.
- 15 is a view showing a release state of a drive pole in a multi-stage transmission of the present invention.
- 16 is a diagram showing a reverse operation of the first forced return means in the multi-stage transmission of the present invention.
- 17 is a view showing a forward operation of the first forced return means in the multi-stage transmission of the present invention.
- FIG. 18 is a perspective view illustrating a pawl in a multistage transmission of the present invention.
- 19 is a diagram showing control of a pole in the multi-stage transmission of the present invention.
- 20 is an exploded perspective view showing the arrangement of springs provided in the first forced return means in the multistage transmission of the present invention
- first speed carrier 413 first speed planetary gear
- control unit 501 second speed first pole
- cabling 531 outer cabling
- drive unit 610 driver
- plate ring 620 drive pole clutch
- cover 750 forced return ring
- FIG. 1 is a perspective view showing a multistage transmission of the present invention
- Figure 2 is a front view showing a multistage transmission of the present invention.
- FIG. 3 is a partially cutaway perspective view showing the multi-stage transmission of the present invention
- FIG. 4 is a front sectional view showing the multi-stage transmission of the present invention.
- FIG. 5 is an exploded perspective view illustrating an exploded hub shell of the multi-stage transmission of the present invention
- FIG. 6 is an exploded perspective view illustrating a third speed planetary gear set of the multi-stage transmission of the present invention
- FIG. 7 is an exploded perspective view of the multi-stage transmission of the present invention.
- FIG. 8 is an exploded perspective view showing an exploded sprocket of the multi-stage transmission of the present invention
- FIG. 9 is an exploded perspective view showing an exploded driver of the multi-stage transmission of the present invention.
- FIG. 10 is an exploded perspective view showing an exploded drive pole clutch of the multi-stage transmission of the present invention
- FIG. 11 is an exploded perspective view showing a first speed planetary gear set of the multi-stage transmission of the present invention.
- FIG. 12 is an exploded perspective view showing the pole of the multi-stage transmission of the present invention
- FIG. 13 is a perspective view showing a control unit of the multi-stage transmission of the present invention.
- Fig. 14 is a view showing the engaged state of the drive poles in the multi-stage transmission of the present invention
- Fig. 15 is a view showing the release state of the drive poles in the multi-stage transmission of the present invention.
- FIG. 16 is a diagram showing a reverse operation of the first forced recovery means section in the multi-stage transmission of the present invention
- FIG. 17 is a diagram showing a forward operation of the first forced recovery means section in the multi-stage transmission of the present invention.
- Fig. 18 is a perspective view showing a pole in the multistage transmission of the present invention
- Fig. 19 is a diagram showing control of a pole in the multistage transmission of the present invention
- Fig. 20 is a first forced return in the multistage transmission of the present invention. It is an exploded perspective view which shows the arrangement of the spring provided in a means part.
- the multi-stage transmission of the present invention implements a multi-stage shift from a planetary gear set by controlling a plurality of poles by stacking control rings, and in addition to the planetary gear set, a drive pole clutch and a drive pole are provided to form a shift stage composed of a planetary gear set. It can be implemented twice, in particular, a forced return means is provided to strongly release the pole that does not come out of strong engagement with the sun gear is a smooth feature that the shift is made smoothly.
- the multi-stage transmission of the present invention includes a shaft 100 fixed at both ends, a sprocket 200 that is rotatably positioned on an outer circumference of the shaft 100, and receives a rotational force, and a hub shell 300 that outputs the rotational force;
- the hub shell 300 includes a planetary gear set including a sun gear, a planetary gear, a carrier, and a ring gear and a one-way clutch provided in the hub shell 300 to shift the rotational force input to the sprocket 200.
- the multi-stage transmission including a control unit 500 for controlling the shift by selectively controlling the rotation of the sun gear by controlling the pole provided in the shaft 100 in accordance with the operation of the shift lever;
- the multi-stage transmission of the present invention is composed of a shaft 100, a sprocket 200, a hub shell 300, a transmission unit 400, and a controller 500.
- the shaft 100 is rotatably fixed to the body of a scooter, a bicycle, a rickshaw or the like (hereinafter, referred to as a “driving device") that requires shifting by means of fastening means such as a fixing nut.
- the shaft 100 is formed with a different diameter according to the part, in particular, the plurality of pole seats 101, 102, 103 formed in the center outer peripheral surface of the shaft 100 concave with a predetermined phase difference
- the pole to be described later is located inside it.
- Such a shaft 100 forms the skeleton of the present invention, and all of the components to be described below are provided on the outer circumference of the shaft 100 to be rotatable or non-rotable.
- the sprocket 200 is configured to receive a rotational force such as an attractive force or electric force from the traveling device into the multi-stage transmission of the present invention, and is provided to be rotatable on one side of the shaft 100.
- the sprocket 200 receives the driving force through a power transmission means such as a chain, for example.
- the hub shell 300 is configured to output the driven force shifted at the outermost position of the shaft 100 to wheels of a traveling device.
- the hub shell 300 is formed in a substantially cylindrical shape, while one side is closed while the other side is opened to insert various components therein through the open portion.
- the hub shell 300 On the closed side of the hub shell 300 is provided a cone nut 902 and a bearing 904 coupled to the shaft 100, the hub shell 300 is rotatably supported independently from the shaft 100. .
- the transmission unit 400 is positioned in the hub shell 300 and shifts the rotation input through the sprocket 200 in multiple stages, and then outputs the plurality of planetary gears through the hub shell 300.
- three planetary gear sets that is, the first-speed planetary gear set 410, the second-speed planetary gear set 420, and the third-speed planetary gear set 430 are provided.
- the first-speed planetary gear set 410 the first-speed planetary gear set 410
- the second-speed planetary gear set 420 the second-speed planetary gear set 420
- the third-speed planetary gear set 430 are provided.
- the transmission part 400 is composed of a first speed planetary gear set 410, a second speed planetary gear set 420, and a third speed planetary gear set 430.
- the rotational force transmitted to the first speed carrier 412 or the first speed ring gear 411 is transmitted to the second speed carrier 422 via the first speed planetary gear set 410 and the second speed carrier 422.
- the rotational force transmitted to) is shifted into six stages through the second speed planetary gear set 420 and the third speed planetary gear set 430, and is output to the hub shell 300.
- Each of the planetary gear sets includes a ring gear, a carrier, a planetary gear, and a sun gear, and the planetary gears are formed in two stages of large and small diameters having different diameters, and are rotatably supported by the carrier.
- a ring gear is provided outside the carrier, and a sun gear is located inside the carrier.
- the first speed planetary gear set 410 may include the first speed ring gear 411, the first speed carrier 412, the first speed planetary gear 413, and the first speed sun gear ( 414).
- the first speed sun gear 414 has a coupling groove formed on its inner circumferential surface so that the rotation is not limited by the pole and is engaged with the outer circumferential surface of the shaft 100 to maintain a fixed state that does not always rotate.
- the third speed planetary gear set 430 may include a third speed ring gear 431, a third speed carrier 432, a third speed planetary gear 433, and a third speed sun gear ( 434).
- the second speed planetary gear set 420 is provided with two sun gears as shown in FIG. 7, the second speed ring gear 421, the second speed carrier 422, the second speed planetary gear 423, And a second first sun gear 424 and a second second second sun gear 425.
- the outer circumferential surface of the second speed first sun gear 424 of the second speed planetary gear set 420 meshes with the large diameter side of the second speed planetary gear 423 having two stages, and the second speed The outer circumferential surface of the second sun gear 425 is engaged with the small diameter side of the second speed planetary gear 423.
- the second speed first sun gear 424, the second speed second sun gear 425, and the third speed sun gear 434 are respectively set to the second speed on the inner gear formed on the inner circumferential surface thereof.
- rotation of the sun gear is selectively limited by the engagement.
- the shift ratio of each planetary gear set is changed according to whether the sun gears are rotatable.
- the first speed carrier 412 of the first speed planetary gear set 410 and the second speed carrier 422 of the second speed planetary gearset 420 are directly connected to each other to rotate integrally;
- the second speed ring gear 421 of the second speed planetary gear set 420 and the third speed carrier 432 of the third speed planetary gear set 430 are directly connected to each other to rotate integrally.
- the driving force transmitted to the transmission unit 400 is transmitted to the third speed planetary gear set 430 from the first speed planetary gear set 410 via the second speed planetary gear set 420 and shifted to multiple stages. After being output through the hub shell 300.
- a plurality of one-way clutches are provided in the shifting part 400, so that when the rotational speed of the component located inside the one-way clutch is faster than the rotational speed of the component located outside, The rotational force of the component is transmitted to the component located outside.
- one-way clutch having such operation is provided with four as shown in FIG. 3.
- a first circle is formed between the outer circumferential surface of the driver 610 of the drive unit 600 and the inner circumferential surface of the first speed ring gear 411 of the first speed planetary gear set 410 provided in the shifting unit 400.
- a second clutch is provided between the outer circumferential surface of the second speed carrier 422 and the inner circumferential surface of the second speed ring gear 421 of the second speed planetary gear set 420 provided in the shifting part 400.
- the wake clutch 920 is provided.
- a third one-way clutch 930 is provided between an outer circumferential surface of the second speed ring gear 421 of the second speed planetary gear set 420 provided in the transmission part 400 and an inner circumferential surface of the hub shell 300.
- a fourth one-way clutch 940 is provided between the outer circumferential surface of the third speed gear ring 431 of the third speed planetary gear set 430 provided in the transmission part 400 and the inner circumferential surface of the hub shell 300.
- the finally shifted rotational force is output to the hub shell 300 only through the third one-way clutch 930 or the fourth one-way clutch 940.
- control unit 500 that controls the shift of the transmission unit 400 includes three poles, that is, a second speed first pole 501, a second speed second pole 502, and a second pole as shown in FIG. 18.
- the three-speed poles 503 are positioned in the pole portions 101, 102, 103 of the shaft 100, respectively, and these poles are positioned to be elastically erected by the ring springs.
- control unit 500 controls one or more poles as one or more poles are stacked and rotated integrally in the axial direction of the shaft 100 as shown in FIG. 12. It is advisable to control the shift by selectively setting the gear to the engaged or released state.
- each pole the control part and the engaging part are formed to protrude at different intervals, and as shown in FIG. 18, first, the second speed first pole 501 and the second speed second pole ( In the drawing, the control section is formed at a predetermined distance from the right end of the drawing, and the locking section is formed again from the control section.
- control section and the engaging portion are adjacent to each other in the second speed first pole 501, whereas the control portion and the engaging portion are the second speed first pole 501 in the second speed second pole 502. It is a little far away from).
- the third speed pole 503 has a control part formed at the right end and a locking part formed at the left end of the drawing, so that the control part and the locking part are farthest apart from each other.
- control ring is located on the control unit formed on each pole, and the sun gear is positioned on the locking portion, respectively.
- the second circumference of the second speed first pole 501, the second speed second pole 502, and the third speed pole 503 rotates in association with the rotation of the shift lever.
- a speed control ring 510 and a third speed control ring 520 are provided along the axial direction of the shaft 100;
- a groove is formed in the inner circumferential surface of the second speed control ring 510 so that the second speed first pole 501 and the second speed second pole 502 are rotated according to the rotation of the second speed control ring 510. This selectively exits into the groove;
- a groove is formed in the inner circumferential surface of the third speed control ring 520 so that the third speed pole 503 selectively exits the groove according to the rotation of the third speed control ring 520.
- the distance between the control section of the second speed first pole 501 and the second speed second pole 502 described above corresponds to the thickness of the third speed control ring 520. .
- the engaging portion of the pole is raised.
- the rotation of the sun gear is to be limited by engaging the inner gear formed on the inner peripheral surface of the corresponding sun gear.
- the groove portion formed in the second speed control ring 510 is formed in a pair corresponding to the second speed first pole 501 and the second speed second pole 502 and the shaft 100.
- a plurality of are formed based on the axial center of;
- a plurality of grooves formed in the third speed control ring 520 are formed on the axis center of the shaft 100 in correspondence with the third speed pole 503.
- the groove portion formed in the second speed control ring 510 is switched between the engagement and release state of the third speed pole 503 every 15 degrees of rotation of the third speed control ring 520, the second speed control The second speed first pole 501 and the second speed second pole 502 that enter the groove of the ring 510 are to be exited from the groove after 30 degrees rotation.
- control unit 500 is connected to the cable is drawn out in accordance with the operation of the shift lever is connected to the cable 530 rotatably supported on the outer peripheral surface of the shaft (100);
- a joint that is elastically transmitted to the spring 590 through the connection ring 541 connected to the cable 530 and the angle control ring 542 fitted and assembled to the connection ring 541 to operate integrally.
- the engagement ring meshes with the joint ring 550 to rotate integrally and rotates the second speed control ring 510 and the third speed control ring 520 in combination with the third speed control ring 520. It is preferred to include 560.
- the cable 530 is an outer cable 531 to which the cable is connected as shown in Figure 8 and the inner cable that is rotatably supported on the shaft 100 in engagement with the inner peripheral surface of the outer cable 531. Ring 532.
- the operating force is transmitted to the joint ring 550 through the coupling ring 541 and the angle control ring 542 as shown in FIG. 11, in which the projection ring protrudes to form the angle control ring ( 542) to rotate integrally.
- a spring 590 is connected between the angle control ring 542 and the joint ring 550 as shown in FIG. 20, so that the joint ring (from the angle control ring 542 through the spring 590). 550 is the operating force is transmitted.
- the control state of 503 is shown in FIG. 19, which is summarized as follows.
- Table 1 below also shows whether or not the one-way clutch transmits the rotational force for each pole operation.
- the drive unit 600 for transmitting the rotational force input to the sprocket 200 to the transmission unit 400 is provided.
- the driver 610 provided in the drive unit 600 is located on the open side of the hub shell 300 as shown in FIG. 9, but is provided with a cone nut 901 and a bearing 903 coupled to the shaft 100.
- the driver 610 is rotatably supported from the shaft 100.
- the hub shell 300 and the drive unit 600 are provided to be rotatable independently from each other by a bearing 905 positioned therebetween, and foreign matters are separated by the dust cover 310 shown in FIG. 8. Prevent intrusion
- bearings 903, 904 and 905 exemplify ball bearings, but are not limited to those types such as sliding bearings.
- the shift is made by selectively transmitting the rotational force through the drive pole 630 between the.
- the rotational force input to the shifting unit 400 is shifted back to the second stage depending on whether the rotation of the drive pole 630 by the drive pole clutch 620 is limited. It is possible.
- the drive pole clutch 620 is a non-rotational component that can only move along the axial direction of the shaft 100 through which a more compact configuration can realize a double speed stage.
- the drive unit 600 is the first of the first speed planetary gear set 410 from the drive unit 600 in accordance with the engagement or release of the drive pole clutch 620 and the drive pole 630.
- the rotational force to the speed carrier 412 or the first speed ring gear 411 is output in two stages can be output with a transmission ratio of 12 stages in total.
- the joint ring 550 is formed with a predetermined section inclined contact surface 551;
- a drive pole clutch 620 positioned outside the connection ring 541 and having an inclined surface 621 corresponding to the inclined contact surface 551 and having a one-way tooth 622 and a contact surface 623 formed on an outer circumferential surface thereof;
- the drive pole clutch 620 meshes with the drive pole clutch 620 in the axial direction of the shaft 100, and an inner circumferential surface engages with the shaft 100, so that the drive pole clutch 620 is not rotatable.
- Rotation limit ring 640 to move along;
- the driver 610 is rotatably supported by the inside of the driver 610 to revolve integrally with the driver 610, the inner end of the drive pole clutch 620 in contact with the revolving contact, the outer end is
- the drive pawl may not be engaged with the teeth formed on the inner circumferential surface of the first speed carrier 412 of the first speed planetary gear set 410 or the drive pole clutch 620 may move in an axial direction to an intermediate position.
- the revolving contact of the driver 610 causes the inner end to repeatedly contact the end of the tooth or the valley of the tooth, forcing the outer end to force the first speed planet.
- the inner end of the drive pole clutch as the drive pole clutch 620 is axially moved to the end position. If the contact surface 623 and the one-way tooth 622 of the latch 620 is out of engagement, the outer end is engaged with the tooth formed on the inner peripheral surface of the first speed carrier 412 of the first speed planetary gear set 410 and the driver. It is preferable to include a drive pole 630 for directly connecting the 610 and the first speed carrier 412 to integrally rotate.
- the drive pole clutch 620 and the rotation limit ring 640 may have a function of the second forced return means.
- Two inclined contact surfaces 551 formed on the joint ring 550 are formed with a phase difference of 180 degrees.
- the inclined surface 621 is formed at one side of the drive pole clutch 620 located at the outer side of the connection ring 541, so that the joint ring 550 rotates so that the inclined contact surface 551 is the inclined surface ( 621, the drive pole clutch 620 moves to the right in the drawing as shown in FIG. 14.
- the spring 580 is connected between the angle control ring 542 and the drive pole clutch 620 as shown in FIG.
- the drive pawl clutch 620 meshes with the rotation limit ring 640, so that rotation is impossible.
- a spring 570 is provided between the drive pole clutch 620 and the rotation limit ring 640 as shown in FIG. 20. To elastically space the gaps.
- the drive pole clutch 620 is elastically supported by the spring 570 to move to the left in the drawing, and the return of the drive pole clutch 620 that has moved to the right is made by the spring 570. You lose.
- the drive pole 630 is provided with an elastic body (not shown) to elastically support the drive pole 630 to rotate in one direction.
- the drive pole 630 rotates together with the drive unit 600, the drive The inner end of the pawl 630 is in contact with the contact surface 623 of the drive pole clutch 620 as shown in FIG.
- the rotational force transmitted through the driver 610-> first one-way clutch 910-> first speed ring gear 411-> first speed planetary gear 411-> first speed carrier 412 The drive force is transmitted to the first speed carrier 412 directly from the driver 610 through the drive pole 630 to transmit the rotational force at a higher speed, so that the drive unit 600 shifts itself by two speeds.
- a total of 12 gears will be realized with 6 gears consisting of three planetary gear sets.
- the shift is formed in the angle control ring 542 in a predetermined angular range so that the shift occurs after the shift lever is rotated by a predetermined angle, and the projection formed in the joint ring 550 is located in the groove. It becomes possible.
- the inner side of the driver 610 is provided with a plate ring 611 which rotates integrally with a predetermined gap; And the drive pole (630) is rotatably supported by the plate ring (611).
- the first forced return capable of selectively controlling the pawl in the engaged state in a forced release state by using the rotational force input to the sprocket 200 according to the rotation operation of the shift lever and the pawl engagement condition.
- the first forced return means 700 is coupled to one surface of the plate ring 611 is rotated integrally and the forward rotating body 710 formed with a ratchet 711 on the inner peripheral surface; Tooth teeth formed on one outer circumferential surface are engaged with the large diameter side of the first speed planetary gear 413 consisting of two stages provided in the first speed planetary gear set 410, and the ratchet 721 is formed on the other inner circumferential surface.
- a rotating body 720 An upper protrusion 731 and a lower protrusion 732 integrally protruding from the rear surface of the joint ring 550; A cover 740 protruding in an arc shape on an upper rear surface of the joint ring 550; Located in the side of the joint ring 550, the upper groove 751 and the lower groove 752 having a predetermined gap for receiving the upper protrusion 731 and the lower protrusion 732 is formed, the elastic adjustment bolt 753 and the compression spring 754 and the compression spring 754 receives the elastic force to the lower groove projection 755 close to a predetermined position by a transfer pin 756 to the center of the lower groove 752 A force return ring 750 for allowing the lower protrusion 732 to be elastically positioned and transmitting an operation force by being coupled to the engagement ring 560; Both sides of the forced return ring 750 are provided to be engaged with the ratchet 711 of the forward rotating body 710 and the ratchet 721 of the reverse rotating body 720,
- the forward rotating body 710 always rotates in the forward direction as shown in FIG. 17, and the reverse rotating body 720 always rotates in the reverse direction as shown in FIG. ).
- the forward pole 760 or the reverse pole 770 provided in the forced return ring 750 is released from the cover 740 of the joint ring 550 to be elastically opened by the elastic body, thereby being located outside thereof.
- the rotational force is transmitted to the forced return ring 750, the shift is made by the shift lever operating force. It is possible to force shifts that were not performed.
- the forced return ring 750 is located between the forward rotation body 710 and the reverse rotation body 720 so that it may be operated in the forward direction or reverse direction, when the shift operation, that is, accelerated operation in the forward direction As shown in FIG. 17, the forward pawl 760 meshes with the ratchet 711 of the forward rotation body 710.
- the transfer pins 756 contacting the lower groove protrusion 755 as shown in FIG. 11 so that the lower protrusion 732 is located at the center from both ends are both sides.
- the transfer pins 756 are elastically supported by the compression springs 754, respectively, and the compression springs 754 are again connected to the elastic adjustment bolts 753 to tighten the elastic adjustment bolts 753. By adjusting or loosening the elastic force of the compression spring 754 may be adjusted.
- the first forced return means 700 can be positioned at the center of the joint ring 550.
- gap retaining rings 810 and 820 are provided to maintain the axial gap with respect to the shaft 100 and rotate around the shaft 100, respectively, such as a third speed sun gear 434.
- the first first sun gear 424, the second second second sun gear 425, and the third second sun gear 434 can be rotated in an unchanged position.
- the drive pole 630 provided in the drive unit 600 only rotates in contact with the contact surface 623 of the drive pole clutch 620, the drive pole 630 to the rotational force of the drive unit 600 is the first speed It does not transfer directly to the first velocity carrier 412 of the planetary gear set 410.
- the rotational force of the driver 610 is transmitted to the first speed ring gear 411 of the first speed planetary gear set 410 through the first one-way clutch 910 provided in the drive unit 600.
- the first speed planetary gear 413 rotates about the fixed first speed sun gear 414
- the second speed carrier of the first speed carrier 412 and the second speed planetary gear set 420 ( 422 rotates integrally.
- the second speed carrier 422 is rotated. Is transmitted to the second speed ring gear 421 through the second one-way clutch 920.
- the third speed carrier 432 of the third speed planetary gear set 430 rotates together with the second speed ring gear 421, but the third speed sun gear 434 is rotatable.
- the planetary gear 433 is unable to transmit the rotational force.
- the second speed control ring 510 and the third speed control ring 520 are rotated about 15 degrees.
- the rotation of the third speed sun gear 434 is limited by engaging with the speed sun gear 434.
- the rotational force of the second speed ring gear 421 is transmitted to the third speed carrier 432.
- the third speed sun gear 434 is restricted by the third speed pole 503, the third speed is reduced.
- the planetary gear 433 rotates to rotate the third speed ring gear 431 at a higher speed than the first stage.
- the rotation of the third speed ring gear 431 is transmitted to the inner circumferential surface of the hub shell 300 through the fourth one-way clutch 940 and output is made.
- the third one-way clutch 930 is To idle.
- the third stage is operated by the shift lever, and as shown in FIG. 19, the second speed control ring 510 and the third speed control ring 520 are further rotated by about 15 degrees. ) Is engaged with the second first sun gear 424 to limit the rotation of the second first sun gear 424.
- the second speed planetary gear having two stages is formed by the rotation of the second speed carrier 422.
- the large diameter side of the gear 423 meshes with the second speed first sun gear 424 to rotate the second speed ring gear 421 at a higher speed than the second stage.
- the third speed carrier 432 of the third speed planetary gear set 430 rotates together with the second speed ring gear 421, but the third speed sun gear 434 is rotatable.
- the planetary gear 433 is unable to transmit the rotational force.
- the joint ring 550 rotates 15 degrees counterclockwise while the forced return ring 750 does not rotate, so that the reverse pole 770 is removed from the cover 740 of the joint ring 550.
- the gear is engaged with the ratchet 721 of the reverse rotation body 720 which rotates in the counterclockwise direction.
- the joint ring 550 rotates 15 degrees clockwise while the forced return ring 750 does not rotate, so that the forward pole 760 is clocked from the cover 740 of the joint ring 550.
- the gear is engaged with the ratchet 711 of the forward rotating body 710 rotating in the direction.
- the fourth gear is operated by the shift lever, so that the second speed control ring 510 and the third speed control ring 520 are further rotated by about 15 degrees.
- a third speed pole 503 meshing with the second speed first sun gear 424 and the third speed sun gear 434, respectively, and the second speed first sun gear 424 and the third speed sun gear 434. ) Is in a state of limiting rotation.
- the rotational force of the second speed ring gear 421 is transmitted to the third speed carrier 432.
- the third speed sun gear 434 is restricted by the third speed pole 503, the third speed is reduced.
- the planetary gear 433 rotates to rotate the third speed ring gear 431 at a higher speed than the three stages.
- the rotation of the third speed ring gear 431 is transmitted to the inner circumferential surface of the hub shell 300 through the fourth one-way clutch 940 and output is made.
- the third one-way clutch 930 is To idle.
- the smooth shift is not performed. If the second speed second pole 502 that is engaged with the second speed second sun gear 425 in the fifth step is not pulled out when the gear shifting from the fifth gear to the fourth gear does not come out smoothly, As described above, a smooth shift is made by the first forced return means 700, and the same description will be omitted since the same forced return operation is performed even in the following shift.
- the fifth gear is operated by the shift lever, and as shown in FIG. 19, the second speed control ring 510 and the third speed control ring 520 are further rotated by about 15 degrees. ) Is engaged with the second speed second sun gear 425 to limit the rotation of the second speed second sun gear 425.
- the second speed planetary gear having two stages is formed by the rotation of the second speed carrier 422.
- the smaller diameter side of the gear 423 meshes with the second speed second sun gear 425 to rotate the second speed ring gear 421 at a higher speed than the fourth gear.
- the third speed carrier 432 of the third speed planetary gear set 430 rotates together with the second speed ring gear 421, but the third speed sun gear 434 is rotatable.
- the planetary gear 433 is unable to transmit the rotational force.
- the sixth gear is operated by the shift lever, and the second speed control ring 510 and the third speed control ring 520 are further rotated by about 15 degrees.
- a third speed pole 503 mesh with the second speed second sun gear 425 and the third speed sun gear 434, respectively, and the second speed second sun gear 425 and the third speed sun gear 434. ) Is in a state of limiting rotation.
- the rotational force of the second speed ring gear 421 is transmitted to the third speed carrier 432.
- the third speed sun gear 434 is restricted by the third speed pole 503, the third speed is reduced.
- the planetary gear 433 rotates to rotate the third speed ring gear 431 at a higher speed than the three stages.
- the rotation of the third speed ring gear 431 is transmitted to the inner circumferential surface of the hub shell 300 through the fourth one-way clutch 940 and output is made.
- the third one-way clutch 930 is To idle.
- the seventh stage is operated by the shift lever, and as shown in FIG. 19, no pole is engaged with the sun gear with the second speed control ring 510 and the third speed control ring 520 further rotated about 15 degrees. It is a state.
- the inclined surface 621 of the drive pole clutch 620 is in contact with the inclined contact surface 551 in the joint ring 550, the rotation angle of which is gradually increased according to the operation of the shift lever, thereby driving the drive pole clutch 620. Is moved to the right in the drawing.
- the drive pole 630 provided in the drive unit 600 is positioned where the one-way teeth 622 are formed through the contact surface 623 of the drive pole clutch 620 and rotated by a predetermined angle, thereby driving the drive pole 630.
- An inner end portion of the inner one end is sandwiched between the one-way teeth 622, the outer end portion is engaged with the inner gear formed on the inner peripheral surface of the first speed carrier 412.
- the drive pole 630 is transferred to the drive pawl 630 directly to the first speed carrier 412 of the first speed planetary gear set 410.
- the rotational force of the driver 610 is transmitted to the first speed carrier 412 of the first speed planetary gear set 410 directly through the drive pole 630, and the first speed carrier 412 and the first speed carrier 412 are transmitted.
- the second speed carrier 422 of the second speed planetary gear set 420 rotates integrally.
- the second speed carrier 422 is rotated. Is transmitted to the second speed ring gear 421 through the second one-way clutch 920.
- the third speed carrier 432 of the third speed planetary gear set 430 rotates together with the second speed ring gear 421, but the third speed sun gear 434 is rotatable.
- the planetary gear 433 is unable to transmit the rotational force.
- the inner end of the drive pole 630 and the drive pawl clutch 620 and the rotation limiting ring 640 corresponding to the second forced return means engage with the contact surface and the one-way tooth 622 of the drive pawl clutch 620.
- the inner end surface is repeatedly contacted with the tip of the tooth or the valley of the tooth by the idle of the driver 610, the outer end is forced to the inner circumferential surface of the first speed carrier 412 of the first speed planetary gear set 410.
- the drive pole 630 is forced to control.
- the eighth to twelveth stages are additionally rotated in steps of about 15 degrees by the second speed control ring 510 and the third speed control ring 520 as shown in FIG. 19.
- the multi-stage transmission of the present invention can be configured in a multi-stage transmission by using a plurality of planetary gear set to improve the productability of the product, the displacement along the axial direction of the shaft 100 according to the operation of the shift lever
- By changing the transmission path of the rotational force through the generated configuration it is possible to double the speed change stage of the multi-stage implemented by the planetary gear set, especially in the forward as well as deceleration operation according to the acceleration operation by using the forced return means.
- According to the reverse operation according to the smooth shift is made is an invention having an excellent advantage that can maximize the ease of use of the user.
- the present invention as described above can be configured in a compact gear by using a planetary gear set to improve the productability of the product, by using the forced return means for the forward operation of the acceleration operation as well as the reverse operation of the deceleration operation It is an invention that can maximize the ease of use of the user by making a smooth shift even.
Abstract
Description
단수 | 제2속 제1폴 | 제2속 제2폴 | 제3속폴 | 드라이브폴 | 원웨이클러치 |
1 | X | X | X | X | 1-2-3 |
2 | X | X | O | X | 1-2-4 |
3 | O | X | X | X | 1-3 |
4 | O | X | O | X | 1-4 |
5 | X | O | X | X | 1-3 |
6 | X | O | O | X | 1-4 |
7 | X | X | X | O | 2-3 |
8 | X | X | O | O | 2-4 |
9 | O | X | X | O | 3 |
10 | O | X | O | O | 4 |
11 | X | O | X | O | 3 |
12 | X | O | O | O | 4 |
Claims (11)
- 양단 고정된 샤프트(100)와, 상기 샤프트(100)의 외주에 회전 가능하게 위치하여 회전력을 입력받는 스프로켓(200) 및 회전력을 출력시키는 허브쉘(300)과;상기 허브쉘(300)의 내부에 마련되는 태양기어, 유성기어, 캐리어, 링기어로 이루어진 유성기어세트와 원웨이클러치를 포함하여, 상기 스프로켓(200)으로 입력되는 회전력을 변속시켜 상기 허브쉘(300)로 출력시키는 변속부(400)와;변속레버의 조작에 따라 상기 샤프트(100)에 마련된 폴을 컨트롤하여 상기 태양기어의 회전을 선택적으로 제한하여 변속을 제어하는 제어부(500)를 포함한 다단 변속기에 있어서;상기 변속레버의 회전 조작에 따라 상기 샤프트(100)의 축방향으로 드라이브 폴 클러치(620)의 변위 발생에 의하여, 회전하는 드라이버(610)와 회전 불가능한 상기 드라이브 폴 클러치(620) 사이의 드라이브 폴(630)을 매개로 하여 회전력을 선택적으로 전달함으로써 변속이 이루어지는 것을 특징으로 하는 다단 변속기.
- 양단 고정된 샤프트(100)와, 상기 샤프트(100)의 외주에 회전 가능하게 위치하여 회전력을 입력받는 스프로켓(200) 및 회전력을 출력시키는 허브쉘(300)과;상기 허브쉘(300)의 내부에 마련되는 태양기어, 유성기어, 캐리어, 링기어로 이루어진 유성기어세트와 원웨이클러치를 포함하여, 상기 스프로켓(200)으로 입력되는 회전력을 변속시켜 상기 허브쉘(300)로 출력시키는 변속부(400)와;변속레버의 조작에 따라 상기 샤프트(100)에 마련된 폴을 컨트롤하여 상기 태양기어의 회전을 선택적으로 제한하여 변속을 제어하는 제어부(500)를 포함한 다단 변속기에 있어서;상기 변속레버의 회전 조작 및 폴의 치합 조건에 따라 상기 스프로켓(200)으로 입력되는 회전력을 이용하여, 치합 상태의 상기 폴을 선택적으로 강제 해제 상태로 제어 가능한 제1강제복귀수단부(700)와; 드라이브 폴 클러치(620) 및 회전제한링(640)으로 이루어져 드라이브 폴(630)을 선택적으로 강제 해제 상태로 제어 가능한 제2강제복귀수단부가 추가 구성되는 것을 특징으로 하는 다단 변속기.
- 양단 고정된 샤프트(100)와, 상기 샤프트(100)의 외주에 회전 가능하게 위치하여 회전력을 입력받는 스프로켓(200) 및 회전력을 출력시키는 허브쉘(300)과;상기 허브쉘(300)의 내부에 마련되는 태양기어, 유성기어, 캐리어, 링기어로 이루어진 유성기어세트와 원웨이클러치를 포함하여, 상기 스프로켓(200)으로 입력되는 회전력을 변속시켜 상기 허브쉘(300)로 출력시키는 변속부(400)와;변속레버의 조작에 따라 상기 샤프트(100)에 마련된 폴을 컨트롤하여 상기 태양기어의 회전을 선택적으로 제한하여 변속을 제어하는 제어부(500)를 포함한 다단 변속기에 있어서;상기 제어부(500)에는 상기 폴을 컨트롤하는 제어링이 상기 샤프트(100)의 축방향으로 한 개 또는 다수가 적층 되어 일체로 회전함에 따라 한 개 또는 다수의 폴을 선택적으로 치합 상태 또는 해제 상태로 컨트롤하여 변속을 제어하는 것을 특징으로 하는 다단 변속기.
- 제 1항 내지 제 3항 중 어느 한 항에 있어서,상기 변속부(400)는 제1속 유성기어세트(410), 제2속 유성기어세트(420), 그리고 제3속 유성기어세트(430)로 구성되며, 드라이브부(600)로부터 제1속 캐리어(412) 또는 제1속 링기어(411)에 전달되어진 회전력을 상기 제1속 유성기어세트(410)를 거쳐서 제2속 캐리어(422)에 전달하고, 상기 제2속 캐리어(422)에 전달된 회전력은 상기 제2속 유성기어세트(420) 그리고 상기 제3속 유성기어세트(430)를 통해 6단으로 변속하여 상기 허브쉘(300)로 출력 가능한 것을 특징으로 하는 다단 변속기.
- 제 4항에 있어서,상기 드라이브부(600)는 상기 드라이브 폴 클러치(620)와 상기 드라이브 폴(630)의 치합 또는 해제에 따라 상기 드라이브부(600)로부터 상기 제1속 유성기어세트(410)의 제1속 캐리어(412) 또는 제1속 링기어(411)로 회전력을 선택적으로 전달하여 2단으로 출력되어 총 12단의 변속비로 출력이 가능한 것을 특징으로 하는 다단 변속기.
- 제 5항에 있어서,제2속 제1폴(501), 제2속 제2폴(502), 그리고 제3속폴(503)의 외주에는 상기 변속레버의 회전에 따라 연동하여 회전하는 제2속 제어링(510) 및 제3속 제어링(520)이 상기 샤프트(100)의 축방향을 따라 적층 마련되되;상기 제2속 제어링(510)의 내주면에는 홈부가 형성되어 상기 제2속 제어링(510)의 회전에 따라 상기 제2속 제1폴(501) 및 상기 제2속 제2폴(502)이 선택적으로 상기 홈부로 빠져 나오며;상기 제3속 제어링(520)의 내주면에는 홈부가 형성되어 상기 제3속 제어링(520)의 회전에 따라 상기 제3속폴(503)이 선택적으로 상기 홈부로 빠져 나오는 것을 특징으로 하는 다단 변속기.
- 제 6항에 있어서,상기 제2속 제어링(510)에 형성되는 홈부는, 상기 제2속 제1폴(501) 및 상기 제2속 제2폴(502)에 대응하여 한 쌍으로 이루어져 상기 샤프트(100)의 축중심을 기준으로 다수 개 형성되며;상기 제3속 제어링(520)에 형성되는 홈부는, 상기 제3속폴(503)에 대응하여 상기 샤프트(100)의 축중심을 기준으로 다수 개 형성되는 것을 특징으로 하는 다단 변속기.
- 제 7항에 있어서,상기 제어부(500)는변속레버의 조작에 따라 인출되는 케이블이 연결되어 상기 샤프트(100)의 외주면에 회전 가능하게 지지되는 케이블링(530)과;상기 케이블링(530)에 연결된 연결링(541) 및 상기 연결링(541)에 끼워맞춤 조립되어 일체로 동작하는 각도 제어링(542)을 통해 스프링(미도시)으로 탄성적으로 조작력을 전달받는 조인트 링(550)과;상기 조인트 링(550)에 치합하여 일체로 회전하며, 상기 제3속 제어링(520)과 결합하여 상기 제2속 제어링(510) 및 상기 제3속 제어링(520)을 회전시키는 치합링(560)을 포함하는 것을 특징으로 하는 다단 변속기.
- 제 8항에 있어서,상기 조인트 링(550)에는 일정 구간 경사접촉면(551)이 형성되며;상기 연결링(541)의 외곽에 위치하되 상기 경사접촉면(551)에 대응하는 경사면(621)이 형성되고 외주면에 일방향 치형(622) 및 접촉면(623)이 형성된 드라이브 폴 클러치(620)와;상기 샤프트(100)의 축방향으로 상기 드라이브 폴 클러치(620)와 치합하고 내주면이 상기 샤프트(100)와 치합하여, 상기 드라이브 폴 클러치(620)를 회전 불가능하게 상기 샤프트(100)의 축방향을 따라 이동 가능하게 하는 회전제한링(640)과;상기 드라이버(610)의 내측에 일정 각도 자전 가능하게 지지되어 상기 드라이버(610)와 일체로 공전하며, 내측 단부가 상기 드라이브 폴 클러치(620)의 접촉면(623)에 접촉하여 공전하며, 외측 단부가 상기 제1속 유성기어세트(410)의 제1속 캐리어(412) 내주면에 형성된 치형에 치합되지 못하거나, 상기 드라이브 폴 클러치(620)가 중간 위치로 축방향 이동에 따라 내측 단부가 상기 드라이브 폴 클러치(620)의 접촉면 및 일방향 치형(622)에 치합될 때, 상기 드라이버(610)의 공전에 의해 내측 단부가 치형의 끝 또는 치형의 골에 반복 접촉되어 강제적으로 외측 단부가 상기 제1속 유성기어세트(410)의 제1속 캐리어(412) 내주면에 치합되지 않거나 치합되는 것을 반복하며, 상기 드라이브 폴 클러치(620)가 끝단 위치로 축방향 이동에 따라 내측 단부가 상기 드라이브 폴 클러치(620)의 접촉면(623) 및 일방향 치형(622)과 치합이 벗어나면 외측 단부가 상기 제1속 유성기어세트(410)의 제1속 캐리어(412) 내주면에 형성된 치형에 치합하여 상기 드라이버(610)와 상기 제1속 캐리어(412)를 직결시켜 일체로 회전하게 하는 드라이브 폴(630)을 포함하는 것을 특징으로 하는 다단 변속기.
- 제 9항에 있어서,상기 제1강제복귀수단부(700)는,상기 플레이트 링(611)의 일면에 적층 결합하여 일체로 회전하며 내주면에 래칫(711)이 형성된 정방향 회전체(710)와;일측 외주면에 형성된 치형이 상기 제1속 유성기어세트(410)에 마련된 2단으로 이루어진 제1속 유성기어(413)의 큰 직경 측에 치합하여 회전하며, 타측 내주면에 래칫(721)이 형성된 역방향 회전체(720)와;상기 조인트 링(550)의 배면에 일체로 돌출 형성된 상측 돌부(731) 및 하측 돌부(732)와;상기 조인트 링(550)의 상측 배면에 원호 형상으로 돌출 형성된 덮개(740)와;상기 조인트 링(550)의 측면에 위치하되, 소정 간극을 갖고 상기 상측 돌부(731) 및 상기 하측 돌부(732)를 수용하는 상측 요홈(751) 및 하측 요홈(752)이 형성되며, 탄성 조절 볼트(753) 및 압축 스프링(754) 및 상기 압축 스프링(754)에 의해 탄성력을 받아 하측 요홈 돌기(755)에 일정 위치까지 밀착되는 전달핀(756)에 의해 상기 하측 요홈(752)의 가운데로 상기 하측 돌부(732)가 탄성적으로 위치되도록 하며, 상기 치합링(560)과 결합하여 조작력을 전달하는 강제 복귀링(750)과;상기 강제 복귀링(750)의 양측에 상기 정방향 회전체(710)의 래칫(711)과 상기 역방향 회전체(720)의 래칫(721)에 각각 치합 가능하게 마련되되, 상기 덮개(740)에 의해 치합이 선택적으로 제한되는 정방향 폴(760) 및 역방향 폴(770)과;상기 정방향 폴(760) 및 상기 역방향 폴(770)을 탄성적으로 일으켜 세우는 탄성체로 구성된 것을 특징으로 하는 다단 변속기.
- 제 10항에 있어서,상기 샤프트(100)에 고정되며, 상기 제2속 제1태양기어(424)와 상기 제2속 제2태양기어(425) 사이 및 상기 제2속 제2태양기어(425)와 상기 제3속 태양기어(434) 사이에 각각 위치하여 제2속 캐리어(422), 제3속 캐리어(432) 및 제2속 제1태양기어(424), 제2속 제2태양기어(425), 제3속 태양기어(434) 등 각각 상기 샤프트(100)에 대하여 축방향 간극을 유지하며 축 중심으로 회전되게 하는 간극유지링(810)(820)이 마련되는 것을 특징으로 하는 다단 변속기.
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US13/980,801 US9182024B2 (en) | 2012-08-09 | 2013-05-31 | Multi-stage transmission |
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KR1020120087145A KR101422135B1 (ko) | 2012-08-09 | 2012-08-09 | 다단 변속기 |
KR10-2012-0087145 | 2012-08-09 |
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KR (1) | KR101422135B1 (ko) |
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TW201514058A (zh) * | 2013-10-14 | 2015-04-16 | Chen zheng he | 二輪載具結構(三) |
CN106972693B (zh) * | 2017-04-07 | 2024-04-05 | 黄善劲 | 一种中置电机和配置该中置电机的电动自行车 |
CN106985960B (zh) * | 2017-05-11 | 2022-09-06 | 张家港川梭车业有限公司 | 一种双前轮直驱棘爪移动换挡变速装置 |
KR101817629B1 (ko) * | 2017-11-23 | 2018-02-21 | (주)엠비아이 | 변속 조작 조력장치 및 이를 구비한 허브 내장형 변속기 |
CN113247169B (zh) * | 2021-06-11 | 2022-09-30 | 天津美派电动科技有限公司 | 一种开关式链轮驱动机构 |
NO347518B1 (en) * | 2021-08-27 | 2023-12-11 | Ca Tech Systems As | Multiple multi-speed gear systems and gear cartridges with different gear ranges and method for manufacturing such |
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- 2013-05-31 US US13/980,801 patent/US9182024B2/en not_active Expired - Fee Related
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KR20140020527A (ko) | 2014-02-19 |
US20150141196A1 (en) | 2015-05-21 |
US9182024B2 (en) | 2015-11-10 |
TW201418600A (zh) | 2014-05-16 |
KR101422135B1 (ko) | 2014-07-22 |
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