WO2016108299A1 - Dispositif de transmission à variation continue - Google Patents

Dispositif de transmission à variation continue Download PDF

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Publication number
WO2016108299A1
WO2016108299A1 PCT/KR2014/012984 KR2014012984W WO2016108299A1 WO 2016108299 A1 WO2016108299 A1 WO 2016108299A1 KR 2014012984 W KR2014012984 W KR 2014012984W WO 2016108299 A1 WO2016108299 A1 WO 2016108299A1
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WO
WIPO (PCT)
Prior art keywords
gear
carrier
chain
planetary gear
guide cone
Prior art date
Application number
PCT/KR2014/012984
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English (en)
Korean (ko)
Inventor
최태수
Original Assignee
주식회사 씨티에스
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Publication date
Application filed by 주식회사 씨티에스 filed Critical 주식회사 씨티에스
Priority to PCT/KR2014/012984 priority Critical patent/WO2016108299A1/fr
Publication of WO2016108299A1 publication Critical patent/WO2016108299A1/fr

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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
    • 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
    • F16H3/46—Gearings having only two central gears, connected by 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
    • F16H9/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members
    • F16H9/26—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members with members having orbital motion

Definitions

  • the present invention relates to a continuously variable transmission, and more particularly, to a continuously variable transmission that can be used for a power transmission device that continuously changes output power to an output side and requires a high capacity of rotational force.
  • 38A and 38B are conceptual views illustrating a double pinion planetary gear device which is a known technique.
  • the double pinion planetary gear device is composed of one sun gear 101, a plurality of carriers 102, a first planet gear 103, a second planet gear 104 and a ring gear 106.
  • the sun gear 101 and the first planetary gear 103 is meshed
  • the first planetary gear 103 and the second planetary gear 104 is meshed
  • the second planetary gear 104 and the ring gear (106) is a match.
  • the sun gear 101 is the same, the first planetary gear 103 is the same, and the second planetary gear 104 is the same.
  • FIG. 38A and 38B when the ring gear 106 is fixed and power is input to the sun gear 101, and power is output to the carrier 102, FIG. Comparing the rotation ratio in (b), the rotation ratio in FIG. 38 (a) is different from the rotation ratio in FIG. 38 (b).
  • the chain 105 is used in place of the ring gear 106 in the double pinion planetary gear device as shown in FIG. 38 (c).
  • the driven second planetary gear 104D and the driven second planetary gear 104F of the driven unit are joined together by a chain 105 having teeth.
  • the drive unit D includes a plurality of driving first planetary gears 103D and a driving carrier shaft 102DS, and a plurality of driving second planetary gears (see FIG. 39 to FIG. 40).
  • 104D and a driving second planetary gear shaft 107D
  • the driven portion F includes a plurality of driven first planetary gears 103F and a driven carrier shaft 102FS, and a plurality of driven second planetary gears 104F.
  • And a driven second planetary gear shaft 107F a driven second planetary gear shaft 107F.
  • the drive first planetary gear 103D rotates on the drive carrier shaft 102DS, and the drive second planetary gear 104D engaged with the drive first planetary gear 103D is on the drive second planetary gear shaft 107D. Since the revolving radius around the driving first planetary gear 103D and the revolving radius around the driving second planetary gear 104D change while rotating, the chain of the driving unit D engaged with the driving second planetary gear 104D ( As the radius of 105 is continuously changed, the rotational speed of the chain 105 of the driving unit D is changed, and the driven second planetary gear 104F of the driven unit F is driven from the engaged chain 105.
  • the driven second planetary gear 104F is engaged with the driven first planetary gear 103F and rotates on the driven second planetary gear shaft 107F while rotating the driven first planetary gear 103F.
  • the peripheral sides of the orbiting radius is the radius of the second planetary gear driven chain (105) of the follower (F) which is engaged on the periphery of (104F) is changed continuously is shifting.
  • the chain 105 is a transmission element such as a chain or a belt having a tooth
  • the chain 105 is a driven second planetary gear 104D and a driven agent. 2 is geared around the planetary gear 104F, and transmits the power of the driving unit D to the driven unit F.
  • the present invention has been made in view of the prior art in that the endless speed change in the stationary state without rotating the transmission element, such as a chain for transmitting power by connecting the drive unit and the follower.
  • the continuously variable transmission system of the prior art is not constituted by two sets of planetary gear units of the driving unit set and the driven unit set, but constitutes the continuously variable transmission system using only one set of the planetary gear units, and accordingly the configuration is simple.
  • the configuration is simple.
  • the present invention provides a transmission system for transmitting power in a set of planetary gear devices and shifting a rotation speed, and a shift adjustment system for adjusting the shift system to obtain a continuous shift ratio.
  • the present invention relates to a continuously variable transmission system comprising a combination of the shift system and the shift adjustment system.
  • the shifting system is a system in which driving force is input to a sun gear and output to a carrier, or driving force is input to a carrier and output to a sun gear, and includes a chain having a sun gear, a carrier, a first planetary gear, a second planetary gear, and a tooth. do.
  • the shift adjustment system is a system for adjusting the output speed by continuously shifting the input rotational speed, wherein at least one of the second planetary gears is constantly in engagement with the chain while the carrier rotates, thereby providing a constant inclination angle.
  • a flange gear, an adjusting sun gear, and an adjusting slider for revolving the second planetary gear about the first planetary gear shaft so as to maintain engagement between the second planetary gear and the chain when the radius of the chain changes. , Adjusting screw, adjusting input gear, helical slider and the like.
  • the continuously variable transmission system may be configured by differently combining the input method and the input method and the output method of the shift system and the shift control system.
  • the configuration is simple and the weight and cost can be reduced by reducing the number of parts, and the engine output (or rotational force) can be used in a power transmission device requiring a high rotational force, that is, the engine It can be applied without limitation to the output of the product, it is durable and simple to configure, and it can save energy by transmitting the rotational force of the input side to the output side with high efficiency.
  • the present invention can be widely applied not only to transport machinery such as automobile, shipbuilding, tiller, bicycle, motorcycle, elevator, but also industrial machinery.
  • FIG. 3 shows a "shifting system (II)" of the present invention.
  • Fig. 6 is a diagram showing a “shift adjustment system” of the present invention.
  • Fig. 9 shows a continuously variable transmission system NO.1 of the present invention.
  • Fig. 10 is an assembled sectional view of the continuously variable transmission system NO.1 in the embodiment of the present invention.
  • Fig. 11 is a view showing the "continuously variable transmission system (NO.2)" of the present invention.
  • Fig. 12 is a view showing the "continuously variable transmission system (NO.3)" of the present invention.
  • Fig. 13 is a view showing the "continuously variable transmission system (NO.4)" of the present invention.
  • 16 is an assembled cross sectional view of the " shifting system I" in the embodiment of the present invention.
  • 17 is a view showing a "shift adjustment system" in an embodiment of the present invention.
  • 19 is an assembled cross sectional view of the "chain 105 and spring set 380" in an embodiment of the present invention.
  • Fig. 21 is an assembly view of the chain 105 and the chain stopper 371 in the embodiment of the present invention.
  • Figure 22 is an assembly view of the spring set 380 in an embodiment of the present invention.
  • Fig. 23 is an assembly view of the flange gear 205, the flange 206 and the flange 207 in the embodiment of the present invention.
  • Figure 24 is a part view of the left carrier 102L and the right carrier 102R in an embodiment of the present invention.
  • 25 is a gear related part view in the embodiment of the present invention.
  • Fig. 26 is a part view of the adjusting main gear 202, the adjusting slider 233, and the adjusting screw 232 in the embodiment of the present invention.
  • Figure 27 is a part view of the helical slider 234 and the adjusting sun gear 204 in the embodiment of the present invention.
  • 29 is a parts view of the left guide cone slider 253L and the right guide cone slider 253R in the embodiment of the present invention.
  • FIG. 30 is a part view of the left guide cone slider screw 254L and the right guide cone slider screw 254R in the embodiment of the present invention.
  • 31 is a component view of the right case cover 11 in the embodiment of the present invention.
  • 34 is a component view of the center case 15 in the embodiment of the present invention.
  • 35 is a part view of the left case cover 14 in the embodiment of the present invention.
  • 36 is a left side view of the guide case 16 in the embodiment of the present invention.
  • reference numerals of the left guide cones are indicated by 251L
  • reference numerals of the right guide cones are indicated by using 251R.
  • the shifting system is classified into four types of shifting system (I), shifting system (II), shifting system (III), and shifting system (IV).
  • shifting system I
  • shifting system II
  • shifting system III
  • shifting system IV
  • continuously variable transmission systems Nos. 1 to 4 are given, and one continuous transmission system (No. 1) will be described as a specific embodiment for easier understanding.
  • the above-described shifting system has a specification of a chain or belt in which the first planetary gear 103 or the second planetary gear 104 is engaged with the second planetary gear 104 depending on whether the step or long pinion, that is, the single-row pinion type, and Since the transmission ratio width can be varied, the present invention is classified into a shift system (I), a shift system (II), a shift system (III), and a shift system (IV) and described with reference to FIGS. 1 to 5 of the present application. do.
  • the configuration eliminates the ring gear in the double pinion planetary gear device and engages the chain 105 or belt with teeth as a substitute for the second planetary gear 104.
  • FIG. 1 the configuration eliminates the ring gear in the double pinion planetary gear device and engages the chain 105 or belt with teeth as a substitute for the second planetary gear 104.
  • the main components are the sun gear shaft 101S, the sun gear 101, the carrier shaft 102S, the first planetary gear 103, the second planetary gear 104, the second planetary gear shaft 107, and the left carrier 102L. ),
  • the chain 105 or the belt has a tooth, and is configured such that the radius can be changed without rotation.
  • the power transmission path can be divided into the following two cases.
  • Case 1 is a case where the chain 105 is stopped, power is input to the sun gear shaft 101S, and output is output from the output gear 111 engaged with the carrier gear 109.
  • Case 2 is a case where the chain 105 is stopped, power is input from the output gear 111 engaged with the carrier gear 109, and output from the sun gear shaft 101S.
  • the first planetary oil assembled with the sun gear shaft 101S and the spline and the fixed sun gear 101 rotates and meshes with the sun gear 101.
  • the gear 103 rotates on the carrier shaft 102S, and the second planetary gear 104 engaged with the first planetary gear 103 rotates on the second planetary gear shaft 107.
  • the second planetary gear shaft 107 is continuously rotated by a predetermined angle about the center of the carrier shaft 102S
  • the second planetary gear 104 is engaged with the first planetary gear 103 in the first planetary gear.
  • the gear 105 is revolved around, and the chain 105 engaged around the second planetary gear 104 does not rotate, but the radius of the chain 105 is continuously changed, where the radius of the chain 105 Is changed but does not rotate, so that the idle speed of the carrier 102 continuously changes and continuously shifts, thereby transferring the changed rotational force to the output gear 111 engaged with the carrier gear 109.
  • the rotational speed of the output carrier gear 109 becomes minimum.
  • the second planetary gear 104 rotating on the second planetary gear shaft 107 is revolved around the first planetary gear 103 by a predetermined angle, and the chain is engaged around the second planetary gear 104. If the radius of 105 is made small, the rotational speed of the output carrier gear 109 becomes large.
  • the difference from the shifting system I of FIG. 1 is that the second planetary gear 104 is formed by applying a multi-row pinion of a step or long pinion, and is not engaged with the second planetary gear 103.
  • the chain 105 is engaged with the pinion in the left row.
  • the characteristics of the shifting system II may vary the type of teeth (for example, roller chain, silent chain, etc.) of the chain 105 and the second planetary gear 104 engaged with the chain 105. It can be applied, and it is possible to widen the choice of conditions (e.g. pitch, number of teeth, etc.) that are limited in the design of the teeth.
  • the power transmission process and the shift principle of the shift system II are the same as the shift system I.
  • the configuration difference from the shifting system I of FIG. 1 is that the first planetary gear 103 is formed by applying a multi-pinion type pinion of a step or long pinion, and a sun gear is applied to the pinion in the right column of the first planetary gear 103. (101) is engaged, and the second planetary gear (104) is engaged with the pinion in the left column.
  • the width ratio of the speed change ratio can be increased by increasing the radius ratio of the chain 105 meshed around the second planetary gear 104.
  • the second planetary gear 104 is formed by applying a multi-row pinion of a step or long pinion, and has both the shifting system II and the shifting system III. Therefore, compared with the transmission system I, the speed ratio width can be increased, and the tooth shape of the chain 105 and the second planetary gear 104 meshed with the chain 105 can be variously applied.
  • the second planetary gear 104 is orbited around the first planetary gear 103, and at least one of the plurality of second planetary gears 104 is always present.
  • This system is called shift control system.
  • the adjustment slider 233 and the adjustment screw 232 are assembled by screws, and the adjustment screw 232 is fixed to the left case cover 14, so that the adjustment slider 233 rotates to the left on the adjustment screw 232. Move in the right or right direction.
  • the helical slider 234 is assembled outside the adjustment slider 233 with two adjustment thrust bearings 231.
  • the adjustment thrust bearing 231 is provided so as not to disturb the rotation of each of the adjustment slider 233 and the helical slider 234.
  • the left carrier 102L connection portion of the helical slider 234 is machined with a spline (or spur gear), and the connection portion of the adjustment sun gear 204 of the helical slider 234 is machined with a screw (or helical gear), so that the helical slider ( The 234 moves in the left or right direction while rotating integrally with the left carrier 102L, and when the helical slider 234 moves in the left or right direction, the adjusting sun gear 204 assembled with a screw (or helical gear) Is rotated so that the left carrier 102L and the adjustment sun gear 204 are rotated.
  • the radius of the chain 105 engaged with the second planetary gear 104 changes simultaneously. At this time, the chain 105 does not rotate, only the radius changes.
  • the guide cone adjusting shaft 256 is assembled with a spline and a guide cone gear 252, a left guide cone adjusting gear 255L and a right guide cone adjusting gear 255R, and are integrally connected to each other.
  • the left guide cone slider screw 254L is fixed to the left guide case 16, and the right guide cone slider screw 254R is fixed to the right case cover 11.
  • the inner diameter of the left guide cone slider 253L is machined and the outer diameter is geared, the screw of the inner diameter is assembled with the left guide cone slider screw 254L, and the gear of the outer diameter is combined with the left guide cone adjusting gear 255L.
  • the inner diameter of the right guide cone slider 253R is machined and the outer diameter is geared, the screw of the inner diameter is assembled with the right guide cone slider screw 254R, and the gear of the outer diameter is connected with the right guide cone adjusting gear 255R.
  • the direction of the screw processed in the left guide cone slider screw 254L assembled with the left guide cone slider screw 254L, and the direction of the screw processed in the right guide cone slider 253R assembled with the right guide cone slider screw 254R Machine them in opposite directions.
  • the guide cone gear 252 rotates
  • the left guide cone adjusting gear 255L and the right guide cone adjusting gear 255R rotate
  • the left guide cone adjusting gear ( 255L) and the left guide cone slider 253L rotates on the left guide cone slider screw 254L in a left or right direction while rotating.
  • the right guide cone slider 253R engaged with the right guide cone adjusting gear 255R rotates and reciprocates in the right or left direction on the right guide cone slider screw 254R.
  • both guide cone sliders reciprocate in opposite directions.
  • the left guide cone 251L is assembled by a spline to the left case 13 so as to slide, and a thrust bearing 257 is inserted between the left guide cone slider 253L.
  • the right guide cone 251R is assembled by a spline to the right case 12 so as to slide, and a thrust bearing 257 is inserted between the right guide cone slider 253R.
  • a chain 105 is installed between the left guide cone 251L and the right guide cone 251R to contact each guide cone on both sides of the chain 105.
  • both guide cones move in the left or right direction without rotation, and the chain 105 does not rotate but only the size of the radius changes.
  • the continuously variable transmission system consists of a combination of a transmission system and a shift adjustment system.
  • four examples of the continuously variable transmission systems Nos. 1 to 4 will be described with reference to FIGS. 9 to 13.
  • the specific assembly installation relationship of the continuously variable transmission system No. 1 will be described as an example so that the present invention can be more reliably understood.
  • the hollow sun gear 101 is assembled with the sun gear shaft 101S and a spline, and the sun gear 101 is fixed to the sun gear shaft 101S.
  • a hollow right carrier 102R is assembled to the right outer diameter of the sun gear 101 from the sun gear shaft 101S, a needle bearing 347 is inserted between the sun gear shaft 101S and the right carrier 102R, and the right carrier 102R is mounted.
  • the thrust bearing 321 is positioned on the left and right sides, and the right case cover 11 is positioned on the right side of the right thrust bearing 321, and the needle bearing (11) is disposed between the right case cover 11 and the sun gear shaft 101S. 344 is inserted, the thrust bearing 321 is positioned on the right side of the right case cover 11, and the circlip 331 is fitted to the sun gear shaft 101S.
  • a hollow adjustment sun gear 204 is assembled on the left side of the sun gear 101, a needle bearing 347 is inserted between the sun gear shaft 101S and the adjustment sun gear 204, and the adjustment sun gear 204 is mounted.
  • the thrust bearing 321 is positioned on the left and right sides of the thrust bearing 321, and the circlip 331 is fitted to the sun gear shaft 101S on the left side of the left thrust bearing 321 to smoothly rotate the adjustment sun gear 204.
  • a hollow adjustment screw 232 is positioned on the left side of the adjustment sun gear 204, a needle bearing 347 is inserted between the hollow adjustment screw 232 and the sun gear shaft 101S, and left and right sides of the adjustment screw 232 are positioned.
  • the thrust bearing 321 is positioned, and the left thrust bearing 321 fixes the circlip 331 to the sun gear shaft 101S to fix the thrust bearing 321 in the inner diameter of the hollow adjustment screw 232. Make it free to rotate.
  • the hollow carrier gear 109 is assembled by splines to the right carrier 102R, and the circlip 335 is fitted to the right carrier 102R to be fixed and engaged with the output gear 111.
  • the output gear 111 engaged with the carrier gear 109 is assembled to the right case cover 11, a needle bearing 344 is inserted between the output gear 111 and the right case cover 11, and the needle bearing (
  • the thrust bearing 321 is positioned on the left and right sides of the 344 and the circlip 331 is inserted into the output gear 111 so that the output gear 111 rotates smoothly in the right case cover 11.
  • the left side of the outer diameter portion of the adjusting sun gear 204 is machined with a screw (or helical gear), and the right side of the inner diameter portion of the helical slider 234 is machined with a screw (or helical gear) and assembled.
  • the right side of the outer diameter portion of the adjusting sun gear 204 is processed into a gear and meshes with the flange gear 205.
  • the outer diameter portion of the helical slider 234 is machined with a spline (or spur gear), and the inner diameter portion of the left carrier 102L is machined with a spline (or spur gear) and assembled together.
  • the helical slider stopper 235 is assembled and fixed with a spline, and the circlip 337 is fitted to the helical slider 234.
  • An adjustment thrust bearing 231 is inserted between the helical slider stopper 235 and the adjustment slider 233, and between the helical slider stopper 235 and the adjustment main gear 202, respectively.
  • the inner diameter portion of the adjustment slider 233 is machined and assembled with the outer diameter portion of the adjustment screw 232, and the outer diameter portion of the adjustment main gear 202 is assembled with the adjustment slider 233 and the spline and connected integrally. And meshes with the adjustment input gear 201.
  • the adjustment slider 233 moves in the left or right direction
  • the helical slider 234 also moves in the left or right direction in the same direction, and the helical slider 234 is rotated integrally with the left carrier 102L to the left.
  • the adjustment sun gear 204 assembled with the helical slider 234 and the screw (or helical gear) rotates the flange gear 205 engaged to the right while rotating by the torsion angle or the helical angle. do. That is, the adjustment sun gear 204 and the left carrier 102L have a rotation difference.
  • the left guide cone slider screw 254L is bolted to the left guide case 16, and a needle bearing 345 is inserted between the inner diameter of the left guide cone slider screw 254L and the left carrier 102L to insert the left carrier 102L. ) To make the rotation smooth.
  • the right guide cone slider screw 254R is bolted to the right case cover 11, and a needle bearing 345 is inserted between the inner diameter of the right guide cone slider screw 254R and the right carrier 102R to insert the right carrier 102R. ) To make the rotation smooth.
  • the first planetary gear 103 engaged with the sun gear 101 is assembled at the center of the outer diameter portion of the carrier shaft 102S, and the needle bearing is disposed between the inner diameter of the first planetary gear 103 and the outer diameter portion of the carrier shaft 102S. 341 is inserted, and thrust bearings 322 are positioned on the left and right sides of the first planetary gear 103.
  • the flange gear 205 welded integrally with the flange 206 on the left side of the first planetary gear 103 is engaged with the regulating sun gear 204 to be assembled with the carrier shaft 102S and the spline, and the first planetary gear 103.
  • the flange 207 is assembled with the carrier shaft 102S as a spline.
  • the thrust bearing 322 is positioned on the carrier shaft 102S between the left side and the left side carrier 102L of the flange gear 205, the needle bearing 343 is inserted into the left side carrier 102L, and the needle bearing (
  • the inner diameter of 343 is assembled by inserting the carrier shaft 102S, and on the left side of the left carrier 102L, the thrust bearing 323 is placed on the carrier shaft 102S, and the circlip 332 is placed on the carrier shaft 102S. Put it on.
  • the thrust bearing 322 is positioned on the carrier shaft 102S between the right side and the right side carrier 102R of the flange 207, the needle bearing 343 is inserted into the right side carrier 102R, and the needle bearing 343 is positioned.
  • the thrust bearing 323 is positioned on the carrier shaft 102S on the right side of the right carrier 102R, and the circlip 332 is placed on the carrier shaft 102S. Put it on.
  • the carrier shaft 102S is free to rotate in the left carrier 102L and the right carrier 102R.
  • the needle bearing 342 is inserted into the inner diameter of the second planetary gear 104 meshed with the first planetary gear 103, and the second planetary gear shaft 107 is inserted into the inner diameter of the needle bearing 342. 2 The rotation of the planetary gear 104 is freed.
  • the thrust bearing 323 is positioned on the second planetary gear shaft 107 on the left side of the second planetary gear 104, and the flange 206 is disposed on the second planetary gear shaft 107 on the left side of the thrust bearing 323.
  • the spline 333 is fitted to the second planetary gear shaft 107 on the left side of the flange 206 to fix the flange 206 and the second planetary gear shaft 107.
  • the thrust bearing 323 is positioned on the second planetary gear shaft 107 on the right side of the second planetary gear 104, and the flange 207 is disposed on the right side of the thrust bearing 323 with the second planetary gear shaft 107.
  • the spline 333 is fitted to the second planetary gear shaft 107 on the right side of the flange 207 to fix the flange 207 and the second planetary gear shaft 107.
  • the chain 105 which maintains concentric circles between the left guide cone 251L and the right guide cone 251R, is meshed with a plurality of second planetary gears 104, and the plurality of second planetary gears 104 are formed in a first manner.
  • the chain 105 does not rotate but changes only a radius.
  • the adjustment input gear 201 places thrust bearings 321 on both sides of the gear portion, and a needle bearing 344 is inserted into the left guide case 16 on the right side, and the adjustment input is made to the inner diameter of the needle bearing 344.
  • the thrust bearing 321 is positioned on the left side and the circlip 331 is inserted into the adjustment input gear shaft 201S.
  • the adjustment input gear 201 is meshed with the adjustment main gear 202 and the guide cone gear 252 so that the adjustment main gear 202 and the guide cone gear 252 also rotate at the same time when the adjustment input gear 201 is rotated. Done.
  • the guide cone adjusting shaft 256 is inserted into the bearing 346 inner diameter so that the guide cone adjusting shaft 256 rotates freely.
  • the guide cone gear 252 is assembled to the guide cone adjusting shaft 256 by splines, and the circlip 339 is fitted into the guide cone gear 252.
  • a left guide cone adjusting gear 255L assembled by spline is connected to the outer diameter of the guide cone adjusting shaft 256, and the right case 12 and the right case Assemble the right guide cone adjusting gear 255R to the outer diameter of the guide cone adjusting shaft 256 between the covers 11 with a spline, and insert the circlip 339 into the guide cone adjusting shaft 256 to adjust the right guide cone adjusting gear.
  • the thrust bearing 322 is positioned on the outer diameter of the guide cone adjusting shaft 256 between the right case 12 and the right guide cone adjusting gear 255R so that the guide cone adjusting shaft 256 is subjected to axial resistance. Rotate smoothly without
  • the outer diameter of the left guide cone slider 253L is machined and geared to the left guide cone adjustment gear 255L, and the inner diameter is machined to be assembled with the left guide cone slider screw 254L to adjust the left guide cone.
  • the gear 255L rotates
  • the left guide cone slider 253L rotates and moves in the left or right direction on the left guide cone slider screw 254L.
  • a left guide cone 251L whose outer diameter is processed into a spline is assembled with the left case 13 and a spline.
  • the left guide cone 251L moves in the left direction or the right direction without rotating at the inner diameter of the left case 13.
  • the thrust bearing 257 is placed in close contact with each other between the left guide cone slider 253L and the left guide cone 251L.
  • the left guide cone 251L also moves by the amount that the left guide cone slider 253L moves in the left direction or the right direction.
  • the outer diameter of the right guide cone slider 253R is machined and geared with the right guide cone adjusting gear 255R, and the inner diameter is machined and assembled with the right guide cone slider screw 254R, adjusting the right guide cone.
  • the gear 255R rotates
  • the right guide cone slider 253R rotates and moves in the left direction or the right direction on the right guide cone slider screw 254R.
  • a right guide cone 251R On the left side of the right guide cone slider 253R, a right guide cone 251R whose outer diameter is processed into a spline is assembled with the right case 12 and a spline, and the right guide cone 251R has an inner diameter of the right case 12. Move in the left or right direction without rotation.
  • the thrust bearing 257 is inserted and positioned between the right guide cone slider 253R and the right guide cone 251R.
  • the right guide cone 251R also moves by the amount that the right guide cone slider 253R moves in the left direction or the right direction.
  • both side surfaces of the chain 105 contact each guide cone surface to maintain concentric circles of the chain 105.
  • the width between the left guide cone 251L and the right guide cone 251R corresponds to a revolving angle between the center of the second planetary gear 104 and the center of the first planetary gear 103 at a constant ratio, but the width of the chain 105 Since the radius does not correspond to a constant ratio, the shape of the left guide cone 251L and the right guide cone 251R, which are in contact with both sides of the chain 105, is curved, so that the radius of the chain 105 changes. The concentric circle is maintained while the chain 105 is engaged with the second planetary gear.
  • each guide cone, the radius of the chain 105 and the idle radius of the second planetary gear 104 are synchronized with the transmission ratio required in the continuously variable transmission system.
  • the center case 15 is positioned between the left case 13 and the right case 12.
  • the left case cover 14, the left guide case 16, the left case 13, the center case 15, the right case 12, and the right case cover 11 are bolted to the cylindrical case. Let's do it.
  • the upper band spring 373 and the band stoppers 375 at both ends of the universal chain 372 are fixed by welding.
  • both side surfaces of the guide plate 374 are manufactured to have an inclination angle.
  • both ends of the chain 105 are engaged at the left and right sides of the chain stopper 371 and are fixed to the chain stopper 371 with the chain fixing cover 376. At this time, the chain 105 fixed to the chain stopper 371 cannot rotate in the radial direction.
  • the assembly state of the spring set 380 is as follows. After the compression spring 385 is assembled into the spring housing 382, the spring stopper 383 is assembled.
  • the hex screw cap 384 is assembled to the spring housing 382.
  • the spring housing 382 is assembled to the center case 15 and screwed to the cylindrical case 17, the spring rod 381 Is assembled to the chain stopper 371.
  • the spring rod 381 and the chain stopper 371 may be integrally connected by a spline or the like.
  • the spring in the spring set 380 when the width between the left guide cone 251L and the right guide cone 251R changes at the same time corresponding to the radius of the chain 105 Both sides of the chain 105 are brought into close contact with the surfaces of the left guide cone 251L and the right guide cone 251R by the tension of 385.
  • Both ends of the chain 105 are meshed with and fixed to the chain stopper 371, so that the chain 105 does not rotate but only changes in radius.
  • the cylindrical case 17, the right case cover 11, the left case cover 14 is filled with oil, thereby smoothly operating the internal parts and improving durability.

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  • General Engineering & Computer Science (AREA)
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  • Transmission Devices (AREA)

Abstract

La présente invention concerne : un système de transmission pour transmettre une puissance par un ensemble de dispositifs à engrenage planétaire et modifier une vitesse de rotation ; un système de commande de transmission pour commander le système de transmission de manière à obtenir un rapport d'embrayage continu ; et un système de transmission à variation continue formé par combinaison du système de transmission et du système de commande de transmission. Le système de transmission est un système dans lequel une force d'entraînement est appliquée par un planétaire et transmise par un support ou dans lequel une force d'entraînement est appliquée par le support et transmise par le planétaire, et qui comprend le planétaire, le support, un premier engrenage planétaire, un deuxième engrenage planétaire et une chaîne ayant une partie dentée.
PCT/KR2014/012984 2014-12-29 2014-12-29 Dispositif de transmission à variation continue WO2016108299A1 (fr)

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020001588A1 (fr) * 2018-06-29 2020-01-02 比亚迪股份有限公司 Transmission, système d'entraînement de puissance et véhicule
CN110715030A (zh) * 2019-09-20 2020-01-21 华中科技大学鄂州工业技术研究院 一种高倍率高精度行星减速器
CN114396464A (zh) * 2022-01-11 2022-04-26 重庆大学 多滚轮式行星牵引减速器
CZ309290B6 (cs) * 2020-11-23 2022-07-27 CSc. Rudněv Alexandr Ing. Převodovka s plynulým převodem

Citations (5)

* Cited by examiner, † Cited by third party
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JPH0669494U (ja) * 1993-03-12 1994-09-30 株式会社椿本チエイン 歯付ベルト又はチェーンを具えた遊星式変速機
JPH09104384A (ja) * 1995-10-11 1997-04-22 M & C Kk 運搬用変速装置
JP2007225103A (ja) * 2006-02-24 2007-09-06 Noriaki Nakajima 遊星歯車とフルードカップリングの自動無段変速装置
KR100899635B1 (ko) * 2008-03-18 2009-05-27 최태수 무단 변속장치
KR101253947B1 (ko) * 2011-05-02 2013-05-07 양건석 유성 스프로킷 체인 감속기

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0669494U (ja) * 1993-03-12 1994-09-30 株式会社椿本チエイン 歯付ベルト又はチェーンを具えた遊星式変速機
JPH09104384A (ja) * 1995-10-11 1997-04-22 M & C Kk 運搬用変速装置
JP2007225103A (ja) * 2006-02-24 2007-09-06 Noriaki Nakajima 遊星歯車とフルードカップリングの自動無段変速装置
KR100899635B1 (ko) * 2008-03-18 2009-05-27 최태수 무단 변속장치
KR101253947B1 (ko) * 2011-05-02 2013-05-07 양건석 유성 스프로킷 체인 감속기

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020001588A1 (fr) * 2018-06-29 2020-01-02 比亚迪股份有限公司 Transmission, système d'entraînement de puissance et véhicule
US11320026B2 (en) 2018-06-29 2022-05-03 Byd Company Limited Transmission, power-driven system, and vehicle
CN110715030A (zh) * 2019-09-20 2020-01-21 华中科技大学鄂州工业技术研究院 一种高倍率高精度行星减速器
CZ309290B6 (cs) * 2020-11-23 2022-07-27 CSc. Rudněv Alexandr Ing. Převodovka s plynulým převodem
CN114396464A (zh) * 2022-01-11 2022-04-26 重庆大学 多滚轮式行星牵引减速器

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