WO2012011662A2 - Transmission à variation continue - Google Patents

Transmission à variation continue Download PDF

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Publication number
WO2012011662A2
WO2012011662A2 PCT/KR2011/004233 KR2011004233W WO2012011662A2 WO 2012011662 A2 WO2012011662 A2 WO 2012011662A2 KR 2011004233 W KR2011004233 W KR 2011004233W WO 2012011662 A2 WO2012011662 A2 WO 2012011662A2
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WO
WIPO (PCT)
Prior art keywords
input link
gear
output
link
links
Prior art date
Application number
PCT/KR2011/004233
Other languages
English (en)
Korean (ko)
Other versions
WO2012011662A3 (fr
Inventor
신용철
신현우
Original Assignee
Shin Young-Chul
Shin Hyun-Woo
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from KR1020100069498A external-priority patent/KR101213546B1/ko
Priority claimed from KR1020100071334A external-priority patent/KR101213547B1/ko
Priority claimed from KR1020110031968A external-priority patent/KR101327336B1/ko
Priority claimed from KR1020110031969A external-priority patent/KR101327332B1/ko
Priority claimed from KR1020110054798A external-priority patent/KR101254596B1/ko
Application filed by Shin Young-Chul, Shin Hyun-Woo filed Critical Shin Young-Chul
Publication of WO2012011662A2 publication Critical patent/WO2012011662A2/fr
Publication of WO2012011662A3 publication Critical patent/WO2012011662A3/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
    • F16H29/00—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action
    • F16H29/02—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between one of the shafts and an oscillating or reciprocating intermediate member, not rotating with either of the shafts
    • F16H29/04—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between one of the shafts and an oscillating or reciprocating intermediate member, not rotating with either of the shafts in which the transmission ratio is changed by adjustment of a crank, an eccentric, a wobble-plate, or a cam, on one of the shafts

Definitions

  • the present invention relates to a continuously variable transmission.
  • the present invention uses a lever crank mechanism for link coupling the input link, the plurality of coupler links and the same number of output links as the number of the coupler links, but the input link is rotated,
  • a variable pin for linking the input link and the plurality of coupler links is elastically fixed in the radial direction of the rotation of the input link according to the load while preventing the rotation and the rotating movement in the state eccentrically arranged at the rotation center of the input link.
  • a plurality of clutch gears externally connected to the output shafts of the plurality of output links through link pins for coupling the plurality of coupler links and the plurality of output links and one-way clutch bearings.
  • the continuously variable transmission having a structure having the same idle center and idling All.
  • the reducer is divided into a constant speed reducer that outputs power at a constant reduction ratio by combining gears of different sizes with each other, and a continuously variable transmission that can change the reduction ratio by applying a conical reduction gear.
  • the rotational force generated from a power generator such as a motor or an engine is output with high rotational power, but the force (torque) is small. Therefore, in most industrial machines, the torque is increased by using a reduction gear.
  • the reducer increases torque instead of slowing down the number of revolutions transmitted from the power generator.
  • the speed reducer reduces the rotation speed supplied from the power generator and increases the torque and outputs the torque.
  • the load applied to the output shaft is greater than the output torque of the output shaft, the load is reversed to the motor or engine that is the power source. By acting, there is a problem of shortening the life of a motor or an engine.
  • a load larger than the output torque of the output shaft acts in a reverse direction to the motor or the engine, thereby preventing a target output from being supplied to the output shaft.
  • the conventional continuously variable transmissions use a lever crank mechanism for linking an input link, a plurality of coupler links, and an output link equal to the number of coupler links to each other, thereby allowing the input link to rotate.
  • a variable pin for link coupling the input link and the plurality of coupler links is to be resiliently moved in the radial direction of the rotation of the input link according to the load while the idle movement in the state eccentrically arranged in the rotation center of the input link Rotating the link pins for linking the plurality of coupler links and the plurality of output links is not idle and the plurality of clutch gears external to the output shaft of the output link via the one-way clutch bearing is not idle It is structured to exercise, the input link and a plurality of Although the variable pin that couples the coupler link is eccentric in the center of the rotational motion of the input link is the most important component for continuously variable speed, but the input link is rotated through the bearing through the bearing,
  • a variable pin that is, the most important component for continuously variable shifting, that is, a pin for linking an input link and a coupler link, is eccentrically disposed at the center of rotation of the input link without idling, and the positioning of the eccentric is structurally determined.
  • the present invention utilizes a lever crank mechanism for link coupling an input link, a plurality of coupler links, and an output link equal to the number of coupler links to each other, wherein the input link is rotated, and the input link and the plurality of input links are rotated.
  • the variable pin for link coupling the coupler link is elastically variable in the radial direction of the rotational motion of the input link according to the load while preventing the rotation and rotational movement in the state eccentrically disposed in the rotation center of the input link,
  • Link pins for linking a plurality of coupler links and a plurality of output links and a plurality of clutch gears external to the output shaft of the plurality of output links via one-way clutch bearings have the same revolution center as the rotation center of the input link.
  • To engage the output gear with the plurality of clutch gears. can be solved by providing a continuously variable transmission having a structure.
  • the present invention is to structurally determine the eccentric positioning of the variable pin, that is, the variable pin for link coupling the input link and the coupler link, which is the most important component for the continuously variable by the problem solving means as described above. It can be done easily.
  • the present invention makes it possible to provide a continuously variable transmission united with a compact unit by the problem solving means as described above, it is possible to provide a hub type continuously variable transmission with a simple appearance without being enlarged externally while the motor is built-in. have.
  • FIG. 1 is a conceptual perspective view showing the continuously variable transmission of the first embodiment
  • FIG. 2 is a cross-sectional view showing a continuously variable transmission based on the conceptual diagram of FIG. 1.
  • FIG. 3 is a sectional view showing a continuously variable transmission of a second embodiment
  • Figure 4 is a front view showing a coupling state between the variable pin and the fixed shaft of Figure 3,
  • FIG. 5 is an enlarged perspective view of the variable pin of FIG. 3;
  • FIG. 6 shows a separate embodiment of FIG. 3,
  • FIG. 7 is a conceptual perspective view showing a continuously variable transmission of a third embodiment.
  • FIG. 8 is a sectional view of a continuously variable transmission based on the concept of FIG. 8;
  • FIG. 9 is a perspective view of an integrated coupler link according to a third embodiment.
  • FIG. 10 is a sectional view of the continuously variable transmission with an integrated coupler link shown in FIG.
  • Fig. 11 is a conceptual perspective view showing the continuously variable transmission of the fourth embodiment.
  • FIG. 12 is a sectional view of a continuously variable transmission based on the concept of FIG.
  • FIG. 13 is a conceptual view illustrating a forward power transmission process and a continuously variable transmission of a continuously variable transmission according to a fourth exemplary embodiment in which a reverse gear and a directional gear are installed.
  • a reverse gear and a directional gear are installed.
  • One of a plurality of clutch gears is provided so that the drawings may not be complicated. Only the clutch gear is shown.
  • FIG. 14 is a conceptual view illustrating a reverse power transmission process of a continuously variable transmission according to a fourth exemplary embodiment in which a reverse gear and a directional gear are mounted, and one clutch among a plurality of clutch gears in order to prevent the drawing from being complicated. Only gears are shown.
  • FIG. 15 is a cross-sectional view of a continuously variable transmission device in which a coupler link shown in FIG. 9 is mounted; FIG.
  • FIG. 16 is a cross-sectional view illustrating another separate embodiment of the continuously variable transmission of the other embodiment shown in FIG. 6.
  • the input link rotates.
  • the variable pin link linking the input link and the plurality of coupler links is elastic in the radial direction of the rotation of the input link according to the external load while preventing the rotation and rotational movement in an eccentrically arranged state in the rotation center of the input link
  • a plurality of link pins externally connected to the output shafts of the plurality of output links via the plurality of link pins linking the plurality of coupler links and the plurality of output links and one-way clutch bearings.
  • FIGS. 1 and 2 are accompanying drawings.
  • the continuously variable transmission of the first embodiment shown in Figs. 1 and 2 has the same number of output links as the number of one input link 60, a plurality of coupler links 90, and the coupler links 90 as in the prior art.
  • the lever crank mechanism which links 70 with each other is included.
  • the input link 60 which is rotatably circumscribed via the bearing 42 on the fixed central axis 21, is rotated by an external drive source 36.
  • One variable pin P1 linking the input link 60 and the plurality of coupler links 90 has a guide rail groove extending radially from the fixed central axis 21 to the fixed central axis 21. 65 is eccentrically inserted at the center of rotation of the input link 60 while being elastically pressed in the radially outward direction by the reaction force S.
  • a plurality of clutch gears 81 circumscribed by 80 are mounted on the input link 60 so as to revolve with the same rotation center as that of the input link 60, as shown in FIG. .
  • the plurality of link pins P2 are spaced apart from each other with the same phase difference in the rotational trajectory of the input link 60, and the plurality of output shafts 80 also have the same phase difference in the rotational trajectory of the input link 60. Are spaced apart.
  • the plurality of clutch gears 81 circumscribed via the one-way clutch bearing 43 on the plurality of output shafts 80 have the same rotation center as the rotation center of the input link 60, and rotate the output gear 82. Is in conflict with
  • External devices to be driven are coupled to the gear unit of the output gear 82 or the drive shaft 83 fixedly inscribed to the output gear 82.
  • the continuously variable transmission configured as in the first embodiment may be operated as follows.
  • the input link 60 is rotated about an axis of the fixed central axis 21 by an external power source.
  • the coupler link 90, the output link 70, the output shaft 80, and the clutch gear 81 mounted on the input link 60 are fixed to the central shaft 21. Orbit around the central axis.
  • the coupler link 90 is coupled to the variable pin (P1) eccentric to the revolving center of the coupler link 90, 0 degrees ⁇ 90 degrees orbital movement of the coupler link 90, 91 degrees ⁇
  • the four coupler links 90 are four outputs linked to each of the four coupler links 90 by 180 degree idle motion, 181 degree 270 degree idle motion, and 271 degree 360 degree idle motion. In the case where one output link 70 of the links 70 is pivoted at an angle for actual driving, the other output link having a phase difference within ⁇ 180 degrees with respect to the one output link 70.
  • coupler links radially outward with respect to the fixed center axis 21 are shown and described as being coupled to the variable pin P1 with a phase difference of 90 degrees
  • At least ten coupler links are linked to the variable pin P1 at a predetermined angle to each other in the circumferential direction of the fixed central axis 21.
  • hapdoel is an implementation which may be substituted as apparent to the art agent.
  • FIG. 3 shows, in cross section, a second embodiment of a hub type continuously variable transmission that can be fixedly inscribed to a hub of a drive wheel, not shown, driven through an electric motor.
  • the hub type continuously variable transmission of the second embodiment includes: a fixed central shaft (21); An electric motor (30) through which the fixed central axis (21) penetrates and is fixedly circumscribed to the fixed central axis (21); And a case 50 rotatably circumscribed to the electric motor 30 via a bearing 41 and fixedly inscribed to a hub of a driving wheel (not shown) and having the electric motor 30 embedded therein.
  • One end of the fixed central axis 21 extends to one side in the direction of the rotational center axis of the case 50, protrudes out of the case 50, and the other end of the fixed central axis 21 is the case 50. It is located in the case 50 extending to the other side in the direction of the center of rotation of the axis.
  • the electric motor 30 is disposed radially inward with respect to the stator 32 and the stator 32 fixedly inscribed in the housing 31 of the electric motor 30, and rotates on the fixed central axis 21.
  • the input gear 34 and the input gear 34 coupled to the rotor 33, the rotor 33, and rotatably circumscribed to the fixed central axis 21.
  • the case 50 includes a reduction gear 35 which rotates with the rotation center and the biased rotation center of the input gear 34.
  • the drum-type input link 60 is rotatably circumscribed with respect to the fixed central shaft 21 in a state of interposing a bearing 42 therebetween.
  • the drum-type input link 60 is rotatably circumscribed in a state in which a bearing 44 is interposed between a boss 51 formed on an inner surface of the case 50 facing the fixed central axis 21. .
  • the drum-type input link 60 may include a first token shape portion 61 and a second token shape portion 62 spaced apart from each other in an axial direction of the fixed central shaft 21, and the first and second token shapes. It includes a fastening member 63 for coupling in a state spaced apart from each other.
  • a ring-shaped rack gear 64 having gears formed on an inner circumferential surface thereof is mounted on an outer rim of the first token-shaped portion 61 of the variable input link 60 facing the reduction gear 35 so that the input link ( It has a rotational center equal to the rotational center of 60 to rotate with the input link (60).
  • a pinion gear 36 is interposed between the rack gear 64 and the reduction gear 35.
  • the pinion gear 36 is coupled to the reduction gear 35 to have the same rotation center as the rotation center of the reduction gear 35 and has a center that is biased with the rotation center of the rack gear 64. Rotating with 35, and is engaged with the gear portion of the rack gear 64 to transfer power to the rack gear (64).
  • the pinion gear 36 is interposed between the rack gear 64 and the reduction gear 35, but as shown in FIG. 6, the reduction gear 35 May be directly engaged with the rack gear 64 so that the reduction gear 25 also acts as a pinion gear.
  • variable pin (P1) movable along is mounted eccentrically at the center of rotation of the input link (60), and the variable pin (P1) is elastic in the direction of rotation of the input link (60) by an external load.
  • the variable pin (P1) to the reaction force device (S; see Fig. 4) such as a spring built in the guide rail groove (65) in a state that the elastically pressing radially outward Is supported by.
  • the input link 60 one end is coupled to the one variable pin (P1) in a state arranged adjacent to the inner surface of the token-shaped portion 61 is radial in the center of rotation of the case 50
  • Four coupler links 90 spaced outwardly and arranged at a phase difference of 90 degrees and one end is coupled to each other end of each of the four coupler links 90 so as to radially outward from the center of rotation of the case 50.
  • Four output links 70 are arranged to be spaced apart by 90 degrees out of phase.
  • Each other end of the four output links 70 is rotatably mounted on an inner surface of the second token shape portion 62 of the input link 60 and radially outward from the center of rotation of the case 50. It is fixedly circumscribed on each of the four output shafts 80 (only two of which are shown in FIG. 8), which are spaced apart by 90 degrees of phase difference.
  • Each of the four output shafts 80 is externally provided with four clutch gears 81 via one-way clutch bearings 43 to receive bidirectional rotational force transmitted to each of the four output links 70 only in one direction.
  • Each of the four clutch gears 81 is rotated in one direction.
  • the one-way clutch bearings 43 are all stepped on the four clutch gears 81 in the same direction, that is, clockwise or counterclockwise, so as to rotate the clutch gear 81 clockwise or counterclockwise. .
  • the boss 51 formed on the inner surface of the case 50 facing the fixed central axis 21 has an output gear 82 fixedly mounted to have the same rotation center as that of the case 50. In this state, the four clutch gears 81 are engaged with all of the four clutch gears 81.
  • the continuously variable transmission of this embodiment having such a configuration is powered and shifted as follows.
  • a coupler link 90, an output link 70, an output shaft 80, and a clutch gear 81 embedded in the input link 60 are fixed to the central shaft 21. Orbit around the central axis.
  • the coupler link 90 is coupled to the variable pin (P1) eccentric to the revolving center of the coupler link 90, 0 degrees ⁇ 90 degrees orbital movement of the coupler link 90, 91 degrees ⁇
  • the four coupler links 90 are four outputs linked to each of the four coupler links 90 by 180 degree idle motion, 181 degree 270 degree idle motion, and 271 degree 360 degree idle motion. In the case where one output link 70 of the links 70 is pivoted at an angle for actual driving, the other output link having a phase difference within ⁇ 180 degrees with respect to the one output link 70.
  • a large load transmitted to the output gear 82 through the driving wheel is transmitted to the reaction force device S through a clutch gear, an output link, a coupler link, and a pin, so that the variable pin P1 is connected to the input link ( 60, the angle of the turning reciprocating motion of the output link 70 becomes smaller so that the clutch gear 81 is in the low speed mode, and conversely, the small transmission from the output gear 82
  • the load is transmitted to the reaction force device S in the same manner as described above, and the variable pin P1 moves away from the center axis of the input link 60, the angle of the turning reciprocating motion of the output links is It becomes large so that the clutch gears are in the high speed mode.
  • the coupler links are linked to the variable pin P1 with a phase difference of 90 degrees.
  • an implementation method in which a plurality of coupler links may be link-coupled to the variable pin P1 with various phase differences is an implementation method that may be obvious to those skilled in the art.
  • the fixed center shaft 21 is a hollow shaft, as shown in FIG.
  • the front end of the hollow portion 22 of the fixed central shaft 21 is able to flow with the guide rail groove 65.
  • the spring 23 is inserted into the hollow portion 22. 3 to 5, the spring 66 and the spring 23 are the reaction means S in the body 66 of the variable pin P1 slidably inserted into the guide rail groove 65. A-shaped groove 67 exposed to the) is formed.
  • reaction means (S) One end of the reaction means (S) is inserted into the L-shaped groove (67) to elastically press the ceiling of the L-shaped groove (67).
  • the tip end of the cam portion 24 whose proximal end is inserted into the tip end of the spring 23 has a tapered cam surface 25 that converges in the center axis direction of the fixed central axis 21.
  • the tapered cam surface 25 is inserted into the L-shaped groove 67 to be in line contact with the ceiling of the L-shaped groove 67.
  • the pressing piece 27 for pressing the base end of the spring 23 is inserted into the hollow portion 22 of the fixed central shaft 21.
  • the base end of the hollow part 22 is screwed, and the bolt 28 which presses the press piece is fastened to the base end of the hollow part 22.
  • the bolt 28 adjusts the elastic pressing amount of the spring 23, adjusts the degree of expansion and contraction of the spring 23, and cooperates with the reaction force (S) the displacement amount of the variable pin (P1) according to the load To make adjustments.
  • variable pin P1 is elastically linearly reciprocally mounted on the fixed center shaft 21 in order to drive the driving wheel in the forward direction by the forward rotational power of the electric motor 30.
  • the variable pin P1 is elastically linearly reciprocated on the fixed center shaft 21 as illustrated in FIG. 6.
  • the variable pin guide portion 21a which is movably mounted, is separately formed, and a one-way clutch 21b is interposed between the fixed central shaft 21 and the variable pin guide portion 21a.
  • the one-way clutch 21b is in a stepped state when the driving wheel is rotated in the forward direction, and the variable pin guide portion 21a is fixed to the fixed center shaft 21, so that the input link 60 is the electric motor 30.
  • the reverse rotational force transmitted to the case 50 fixedly inscribed at the cutting edge is cut by the clutch gear 81 via the output gear 82, but the one-way clutch interposed between the clutch gear 81 and the output shaft 80.
  • the driving force in the forward rotation direction of the motor when the driving force in the forward rotation direction of the motor is applied, it is fixed to the output unit in the state capable of continuously shifting by the lever crank mechanism without rotating the variable pin and idle.
  • the rotational force in the rotational direction is applied and the driving force in the reverse rotational direction of the motor is applied, the input link holding the lever crank mechanism while rotating the variable pin while rotating the variable pin is rotated in the reverse rotational direction so that the output section
  • a reverse drive means for imparting rotational force it is possible to transmit the reverse rotational drive force to the output unit.
  • the reverse drive means is as follows.
  • FIG. 16 is a cross-sectional view of yet another embodiment of a hub type continuously variable transmission provided with the reverse drive means.
  • the reverse driving means is added in addition to the configuration of the second embodiment shown in FIG. 3 and the other embodiment shown in FIG. In the following, only the reverse drive means will be described.
  • the boss 51 formed on the inner surface of the case 50 facing the fixed center axis 21 is fixedly mounted to the final output shaft 85 to have the same rotation center as that of the case 50.
  • the output gear 82 meshed with all the four clutch gears 81 is fixedly circumscribed on the final output shaft 85.
  • At least one of the four output shafts 80 is externally provided with a first intermediate gear 87 via a one-way clutch bearing 86, and the final output shaft 85 is interposed with a one-way clutch bearing 88.
  • the second intermediate gear 89 is circumscribed, and the third intermediate gear 84 is circumscribed on the final output shaft 85.
  • the first intermediate gear 87 is provided with two gear portions 87a and 87b to be engaged with the second and third intermediate gears 89 and 84 simultaneously.
  • the one-way clutch bearings 43 are all stepped on the four clutch gears 81 in the same direction, and transmit power to the clutch gear 81 in the reverse rotation direction when the output shaft 80 rotates in the reverse direction. In the forward rotation of the clutch gear 81, power is transmitted to the output shaft 80 in the forward rotation direction.
  • the one-way clutch bearing 86 transmits power to the first intermediate gear 87 in the reverse rotation direction when the output shaft 80 is reversely rotated, and at the forward rotation of the first intermediate gear 87, the output shaft ( 80) to transmit power in the forward direction.
  • the one-way clutch bearing 88 transmits power to the second intermediate gear 89 in the forward rotation direction at the time of forward rotation of the final output shaft 85 and at the end of the reverse rotation of the second intermediate gear 89. Power is transmitted to the output shaft 85 in the reverse rotation direction.
  • the third intermediate gear 84 rotates in the forward direction
  • the second intermediate gear 89 of the final output shaft 85 rotates in the forward rotation direction. Done.
  • first and second intermediate gears 87 and 89 smoothly mesh with each other as the first intermediate gear 87 rotates in the reverse rotation direction and the second intermediate gear 89 rotates in the forward rotation direction. Will rotate.
  • the clutch gear 81 and the first intermediate gear 87 is in a stopped state, the state that can not transmit power to the final output shaft 85 do.
  • the other one of the four output shafts 80 is in the reverse rotation state, the final output shaft 85 is rotated in the forward direction, accordingly, the clutch gear 81 is the final output shaft 85 By the reverse rotational power, but the clutch gear 81 and the one-way clutch bearing 86 is in a sliding state so that the clutch gear 81 is rotated in reverse and the one output shaft 80 is in a stopped state.
  • the first intermediate gear 87 also rotates in a reverse rotation direction without transmitting power to the one output shaft 80
  • the second intermediate gear diagram 89 also includes the first intermediate gear diagram 89.
  • the intermediate gear 87 is rotated in the forward direction while being engaged with the intermediate gear 87.
  • the continuously variable transmission of the embodiment having such a configuration is powered and shifted as follows.
  • the coupler link 90 is coupled to the variable pin (P1) eccentric to the revolving center of the coupler link 90, 0 degrees ⁇ 90 degrees orbital movement of the coupler link 90, 91 degrees ⁇
  • the four coupler links 90 are four outputs linked to each of the four coupler links 90 by 180 degree idle motion, 181 degree 270 degree idle motion, and 271 degree 360 degree idle motion. In the case where one output link 70 of the links 70 is pivoted at an angle for actual driving, the other output link having a phase difference within ⁇ 180 degrees with respect to the one output link 70.
  • variable pin (P1) is also eccentric from the center axis of the fixed center axis 21 is subjected to a load by the reverse rotation of the input link 60, to accommodate the variable pin (P1)
  • the variable pin guide portion 21a is also subjected to a load in the reverse rotation direction, so that the one-way clutch bearing 21b is in a non-walking state, and the variable pin P1 is idle in the reverse rotation direction, and the variable The pin guide portion 21a rotates in the reverse rotation direction.
  • the lever crank mechanism composed of the input link 60, the coupler link 90, the output link 70, the output shaft 80, and the clutch gear 81 does not perform a link movement so that the clutch gear 81 Orbital movement in the reverse direction, and thus the final output shaft 85 that is engaged to the four clutch gear 81 at the same time is to rotate in the reverse direction.
  • the electric motor 30 gives the reverse rotational power
  • the final output shaft 85 is rotated in the reverse direction without stepless speed
  • the case 50 is rotated in the reverse direction
  • the case 50 The driving wheel fixedly circumferentially rotates in the reverse direction.
  • the first intermediate gear 87 is described as being circumscribed via a one-way clutch bearing 86 on one output shaft 80, but stable driving of the continuously variable transmission, i.e., balanced For driving, another first intermediate gear may be circumscribed through the one-way clutch bearing in the other output shaft 80 arranged with a phase difference of 180 degrees with respect to the one output shaft 80, and all the output shafts 80 ), The first intermediate gear may be circumscribed through the one-way clutch bearing.
  • the continuously variable speed transmission apparatus of the third embodiment includes an input link 100 receiving a rotational force input from the outside;
  • the rotation center axis X of the input link 100 in a state where the rotation center is eccentric to the rotation center axis X of the input link 100 and has a predetermined distance from each other in the circumferential direction of the input link 100.
  • a plurality of output links 110 rotatably mounted to the input link 100 while revolving around the input link;
  • the fixed shaft 200 having the same center axis as the rotation center axis line X of the input link 100 is formed.
  • An annular output shaft 300 rotatably circumscribed on an outer circumferential surface; Of the fixed shaft 200 for accommodating the reaction force device S that elastically presses the variable pin P1 that is variable in the radial direction by an external load in the radially outward direction together with the variable pin P1.
  • a guide rail groove 130 provided at one end;
  • a plurality of coupler links 140 having the same length, one end of which is coupled to the variable pin P1 of the guide rail groove 130, and the other end of which is coupled to the other end of each of the plurality of output links 110. Include.
  • the input gear (G1) is fixedly circumscribed.
  • the plurality of output links 110 may include a plurality of branch input links 101 extending parallel to the rotation center axis X in a state in which the plurality of output links 110 are eccentrically disposed with respect to the rotation center axis X of the input link 100. Is rotatably circumscribed.
  • annular drive shaft 300 is fixed to the output gear (G3) meshing with all of the plurality of clutch gear (G2) and the other end, as shown in Figure 8, the power to the outside
  • the final output gear G4 to transmit is fixedly circumscribed.
  • the one-way clutch bearings 120 include the plurality of clutch gears when the plurality of clutch gears G2 rotate in one direction while the plurality of output links 110 are rotated in a non-rotating or other direction.
  • the plurality of output links 110 rotate in the other direction in a state in which G2 steps with the plurality of output links 110 or the plurality of clutch gears G2 rotates in a non-rotating or one direction.
  • the plurality of clutch gears G2 are stepped with the plurality of output links 110 when turned).
  • the one-way clutch bearings 120 may be configured to rotate when the plurality of clutch gears G2 rotate in the other direction in a state in which the plurality of output links 110 rotate freely or rotate in one direction.
  • Two clutch gears G2 are freely rotated in the other direction with respect to the plurality of output links 110 by not walking with the plurality of output links 110, or the plurality of clutch gears G2 are not rotated.
  • the plurality of clutch gears G2 do not walk with the plurality of output links 110 when the plurality of output links 110 are rotated in one direction while being rotated in another direction.
  • the output link 110 is free to rotate in the other direction.
  • variable pin P1 is eccentrically positioned at the center of rotation X of the input link 100, which is the revolving center of the output link 110, by the reaction force S in the guide rail groove 130. It is positioned.
  • reaction force device S of the guide rail groove 130 may not only be an elastic spring but also a pneumatic pressure connected to a hydraulic or pneumatic circuit for advancing and reversing the cylinder according to the load transmitted to the reaction force device S. It can be a cylinder or a hydraulic cylinder.
  • the continuously variable transmission according to the third exemplary embodiment of the present invention rotates on the variable pin P1 instead of the plurality of coupler links 140 shown in FIG. 7 as shown in FIGS. 9 and 10.
  • Possible to circumscribe the central portion 151 and the central portion 151 in the circumferential direction to each other in the circumferential direction and to extend the same length in the radial outward direction to insert the other end of the output link 110 and the link coupling pin An integrated coupler link 150 composed of a plurality of link portions 153 in which an arcuate long hole 152 is formed may be used.
  • a bearing 154 is interposed in the central portion 151 of the integrated coupler link 150. Accordingly, the rotational friction force between the variable pin P1 and the central portion 151 may be minimized by the bearing 154. have.
  • the continuously variable transmission of the third embodiment having such a configuration is powered and shifted as follows.
  • the plurality of clutch gears G2 transmits the clockwise rotational force to the output gear G3 meshed with the plurality of clutch gears G2, and thus is in a state of rotating clockwise, but the plurality of output links
  • the plurality of clutch gears G2 are connected to the plurality of output links by the one-way clutch bearing 120.
  • the output gear G3 is rotated clockwise by the revolution of the clock gears of the plurality of clutch gears G2.
  • the output shaft 300 is rotated once with respect to one rotation of the input link 100.
  • the output link 110 is link coupled to the coupler links 140 and 150 coupled to the variable pin P1 eccentrically positioned at the idle center of the output link 110, the output When the link 110 revolves clockwise, the output link 110 is rotated reciprocating clockwise and counterclockwise by the principle of the lever crank mechanism.
  • the clutch gear G2 when the output link 110 is rotated in the clockwise direction, the clutch gear G2 is in a non-rotating state and the output link 110 is rotated in the clockwise direction, that is, one-way clutch 120
  • the clutch gear (G2) and the output link 110 is in a non-stepped state by), the clutch gear (G2) is unable to transmit a driving force to the output gear (G3), and the output link
  • the clutch gear G2 When 110 is rotated counterclockwise, the clutch gear G2 is in a non-rotating state and the output link 110 is rotated counterclockwise, that is, by the one-way clutch 120.
  • the gear G2 and the output link 110 are in a walking state, and the clutch gear G2 is rotated counterclockwise with the output link 110 to rotate the output gear G3 clockwise. Will be driven.
  • the clutch gear G2 transmits the driving force to the output gear G3 in the clockwise direction by the rotation and the rotational rotation, and eventually the plurality of clutch gears G2 are successively connected to the output gear G3 in the clockwise direction.
  • the driving force is transmitted to the output gear, whereby the output gear G3 makes one or more rotations with respect to one rotation of the input link 100.
  • the external load transmitted to the annular output shaft 300 is output gear (G3), a plurality of clutch gear (G2), output link 110, a plurality of coupler links 140 or integral coupler links 150. And transmitted to the reaction force device S through the variable pin P1, so that the variable pin P1 is closer to the rotational center axis X of the input link 100, which is the revolving center of the output link 110. Since the angle of the turning reciprocating motion of the output link 110 approaches 0, the clutch gear G2 is in the low speed mode, and the external load transmitted from the annular output shaft 300 has the reaction force device in the same manner as described above.
  • variable pin (P1) is farther away from the rotational center axis (X) of the input link 100, which is the revolving center of the output link 110, the angle of the turning reciprocating motion of the output link 110 Becomes large, and the clutch gear G2 enters the high speed mode.
  • the third embodiment although three output links radially outward with respect to the input link 100 are shown and described as being coupled to the variable pin P1 with a phase difference of 120 degrees, the first embodiment is described. As described in the example, various numbers of output links may be linked to the variable pin P1 at a predetermined angle to each other in the circumferential direction of the input link 100.
  • the continuously variable transmission of the fourth embodiment adds a configuration by revolving the variable pin (P1) to the basic principle configuration of the first to third embodiments, thereby continuously providing an output device with an output speed more than the input speed to the external device. Device.
  • the continuously variable speed transmission apparatus of the fourth embodiment includes an input link 100 receiving a rotational force input from the outside;
  • the rotation center axis X of the input link 100 in a state where the rotation center is eccentric to the rotation center axis X of the input link 100 and has a predetermined distance from each other in the circumferential direction of the input link 100.
  • a plurality of output links 110 rotatably mounted to the input link 100 while revolving around the input link;
  • the fixed shaft 200 having the same center axis as the rotation center axis line X of the input link 100 is formed.
  • An output shaft 300 rotatably circumscribed on the outer circumferential surface;
  • a reaction force (S) for urging the variable pin (P1) variable in the radial direction outwardly in the radial direction by an external load with the variable pin (P1) of the fixed shaft (200) A guide rail groove 130 provided at one end;
  • a plurality of coupler links 140 having the same length, one end of which is coupled to the variable pin P1 of the guide rail groove 130 and the other end of which is coupled to each other of the plurality of output links 110;
  • the fixed shaft is rotatably mounted to the input link 100 in a state that the rotation center axis of the input link 100 is less eccentric than the eccentric amounts of the plurality of output links 110.
  • the input gear (G1) is fixedly circumscribed.
  • the plurality of output links 110 may include a plurality of first branch input links extending in parallel with the rotation center axis X in a state that the plurality of output links 110 are eccentrically disposed with respect to the rotation center axis X of the input link 100. It is circumscribed rotatably at 101.
  • annular drive shaft 300 is fixed to the output gear (G3) engaging all of the plurality of clutch gear (G2) and the other end, as shown in Figure 12, the power to the outside
  • the final output gear G4 to transmit is fixedly circumscribed.
  • the step relation between the plurality of clutch gears G2 and the plurality of output links 110 by the first one-way clutch bearings 120 is the same as in the third embodiment.
  • the guide rail groove 130 may be externally or internally rotatably connected to one end of the fixed shaft 200.
  • the guide rail groove 130 is rotatably rotated at one end of the fixed shaft 200. It is shown to be inscribed.
  • the reaction force device S of the guide rail groove 130 may not only be an elastic spring but also a pneumatic cylinder connected to a hydraulic or pneumatic circuit for advancing and retracting the cylinder according to the load transmitted to the reaction force device S. It can be a hydraulic cylinder.
  • variable pin P1 is eccentrically positioned at the rotational center axis X of the input link 100, which is the revolving center of the output link 110, by the reaction force device S in the guide rail groove 130. It is positioned at.
  • the rotating unit 400 rotates to the second branch input link 102 extending in parallel with the rotation center axis X in a state that the rotation unit 400 is eccentrically disposed with respect to the rotation center axis X of the input link 100. Possibly circumscribed.
  • the reverse gears G7 and 12 are circumscribed through the second one-way clutch bearing 122 in the rotating part 400.
  • the input link 100 is rotatably mounted to the input link 100 in a state that the input link 100 is eccentric with respect to the rotational center axis X of the input link 100 so as to simultaneously fit the reverse gear G7 and the output gear G3.
  • the physics further includes a turning gear G8 (see Fig. 13).
  • the divert gear G8 extends in parallel with the rotation center axis X in a state in which the direction change gear G8 is eccentrically disposed with respect to the rotation center axis X of the input link 100.
  • 103 (see Fig. 7) is rotatably circumscribed.
  • the second one-way clutch bearing 122 rotates the reverse gear G7 when the reverse gear G7 is rotated non-rotatingly or in one direction while the rotating part 400 is rotated in the other direction. And rotates in the other direction together with the rotating part 400, or when the rotating part 400 is rotated in the other direction in a state in which the reverse gear G7 is rotated non-rotatingly or in one direction. G7 is stepped on the rotating part 400 to rotate in the other direction together with the rotating part 400.
  • the second one-way clutch bearing 122 may rotate the reverse gear G2 when the reverse gear G2 is rotated in a non-rotating or other direction while the rotating part 110 is rotated in one direction.
  • the rotating unit 400 is rotated in the other direction without rotation or free rotation with respect to the rotating unit 400 so as not to walk with the rotating unit 400, or in the state in which the reverse gear G7 is rotated in the non-rotating or other direction.
  • the reverse gear G7 is not rotated with the rotary part 400 so as to rotate freely with respect to the rotary part 400 in the other direction, or the rotating part in a state in which the reverse gear G7 is rotated in the other direction.
  • the reverse gear G7 is not rotated with the rotating part 400 so as to freely rotate in the other direction with respect to the rotating part 400.
  • the second one-way clutch bearing (122) is rotated in one direction when the reverse gear (G7) is rotated in a state in which the rotating unit (400) rotates in one direction.
  • the reverse gear G7 is not rotated with the rotary part 400 so as to rotate freely with respect to the rotary part 400 in one direction, or the rotary part 400 in a state in which the reverse gear G7 is rotated in one direction.
  • Rotates in one direction the reverse gear (G7) is not rotated with the rotating part 400 so as to freely rotate in the other direction with respect to the rotating part (400).
  • the continuously variable transmission of the fourth embodiment having such a configuration is powered and shifted as follows.
  • the plurality of clutch gears G2 and the plurality of output links 110 are connected to the input link. Receiving the rotational force of the (100) is rotated in the forward direction (A direction) around the center of rotation axis (X) of the input link (100).
  • the plurality of clutch gears G2 transmits forward rotational force to the output gears G3 engaged with the plurality of clutch gears G2, and thus, the plurality of clutch gears G2 are rotated in the forward direction.
  • the non-rotating state, the plurality of clutch gear (G2) is to rotate in the forward direction, the first one-way clutch bearing 120, the plurality of clutch gear (G2) is the plurality of output links (
  • the output gear G3 is rotated in the forward direction by the forward revolution of the plurality of clutch gears G2.
  • the rotation unit 400 also receives the rotational force of the input link 100 is revolved in the forward direction about the axis of rotation axis (X) of the input link 100.
  • the first planetary gear G5 ′ fixedly circumscribed to the rotating part 400 is engaged with the fixed gear G5 circumscribed to the fixed shaft 200 while being centered on the second branch input link 102. It rotates forward with respect to the axis, and accordingly, the second planetary gear G6 ′ fixedly circumscribed to the rotation part 400 also rotates forward about the center axis of the second branch input link 102. .
  • the sun gear G6 meshed with the second planetary gear G6 ′ rotates in a reverse direction about the rotational center axis X of the input link 100 by the second planetary gear G6 ′. Accordingly, the guide rail groove 130 also rotates in a reverse direction about the rotation center axis line X of the input link 100.
  • variable pin P1 revolves about the rotational center axis X of the input link 100 in the reverse direction.
  • the output link 110 is coupled to the variable pin (P1), the reciprocating rotation in the forward and reverse directions by the orbital movement of the variable pin (P1).
  • the clutch gear G2 and the output link 110 is not walked by the first one-way clutch bearing 120,
  • the clutch gear G2 does not transmit the driving force to the output gear G3, and when the output link 110 pivots in the reverse direction, the clutch gear is driven by the first one-way clutch 120.
  • G2 and the output link 110 are in a walking state, and the clutch gear G2 pivots in the reverse direction together with the output link 110 to drive the output gear G3 in the forward direction. .
  • the clutch gear G2 transmits the driving force to the output gear G3 in the forward direction by the revolution and the rotational rotation.
  • the plurality of clutch gears G2 are successively connected to the output gear G3 in the forward direction.
  • the driving force is transmitted to the output gear, whereby the output gear G3 makes at least one rotation in the forward direction with respect to one rotation of the input link 100.
  • the external load transmitted to the annular output shaft 300 is output gear (G3), a plurality of clutch gear (G2), output link 110, a plurality of coupler links 140 or integral coupler links 150. And transmitted to the reaction force device S through the variable pin P1, the closer the variable pin P1 is to the rotational center axis X of the input link 100 that is the revolving center of the output link 110. Since the angle of the turning reciprocating motion of the output link 110 approaches 0, the clutch gear G2 is in the low speed mode, and the external load transmitted from the annular output shaft 300 has the reaction force device in the same manner as described above.
  • variable pin (P1) is farther away from the rotational center axis (X) of the input link 100, which is the revolving center of the output link 110, the angle of the turning reciprocating motion of the output link 110 Becomes large, and the clutch gear G2 enters the high speed mode.
  • the continuously variable transmission apparatus transmits power and shifts in the forward direction as follows in the state in which the reverse gear G7 and the direction change gear G8 are mounted.
  • the output gear G3 makes one rotation or more in the forward direction with respect to one rotation of the input link 100.
  • the turning gear G8 meshed with the output gear G3 receives the forward rotational force of the output gear G3 and rotates in a reverse direction about a center axis of the third branch input link 103.
  • the reverse gear G7 engaged with the turning gear G8 receives the reverse rotational force of the turning gear G8 in the same forward direction as the rotation direction of the rotating part 400, so that the second branch input link 102 Rotate around the central axis of).
  • the reverse gear (G7) is rotated in the forward direction in the state in which the rotating unit 400 is rotated forward, so that the second one-way clutch bearing 122 is in a state that does not walk with the rotating unit (400)
  • the rotating unit 400 is freely rotated in the forward direction.
  • the external load transmitted to the annular output shaft 300 is output gear (G3), a plurality of clutch gear (G2), output link 110, a plurality of coupler links 140 or integral coupler links 150. And it is transmitted to the reaction force device (S) through the variable pin (P1), as described above, the output gear (G3) is a stepless speed change occurs above the rotation speed of the input link (100).
  • the continuously variable transmission apparatus is power-transmitted in the reverse direction as follows in the state in which the reverse gear G7 and the direction change gear G8 are mounted.
  • the plurality of clutch gears G2 transmit a reverse rotational force to the output gears G3 meshed with the plurality of clutch gears G2, and thus are in a state of rotating in the reverse direction.
  • the first one-way clutch bearing 120, the plurality of clutch gear (G2) is the plurality of output links ( It is in a state where it does not walk with 110, and rotates freely in the reverse direction with respect to the plurality of output links 110.
  • the output gear G3 does not receive the rotational force of the plurality of clutch gears G2.
  • the rotation unit 400 rotatably circumscribed to the second branch input link 102 and the turning gear G8 rotatably circumscribed to the third branch input link 103 are also the input link 100.
  • the rotational force of the input link 100 is rotated in the reverse direction around the center of rotation axis (X) of the input link.
  • the first planetary gear (G5 ') fixedly circumscribed to the rotating unit 400 is engaged with the fixed gear (G5) fixedly circumscribed to the fixed shaft 200, the center axis of the second branch input link (102)
  • the second planetary gear G6 ′ fixedly circumscribed to the rotation unit 400 also rotates in a reverse direction about the central axis of the second branch input link 102.
  • the sun gear G6 meshed with the second planetary gear G6 ' is rotated forward by the second planetary gear G6' about the center of rotation axis X of the input link 100. Accordingly, the guide rail groove 130 also rotates in the forward direction about the rotation center axis line X of the input link 100.
  • variable pin (P1) is forward orbit around the center of rotation axis (X) of the input link (100).
  • the clutch gear G2 when the output link 110 is pivoting in the forward direction, the clutch gear G2 is in a reverse rotation state and the output link 110 is pivoting in the forward direction, that is, the first one-way clutch bearing ( By the 120, the clutch gear G2 and the output link 110 are in a non-walking state, and the clutch gear G2 cannot transmit a driving force to the output gear G3, and the output link
  • the clutch gear G2 When 110 is pivoted in the reverse direction, the clutch gear G2 is in the reverse rotation state and the output link 110 is pivoted in the reverse direction, that is, the first gear clutch 120 by the first one-way clutch 120. (G2) and the output link 110 is in a non-walking state, the clutch gear (G2) is unable to transmit the driving force to the output gear (G3).
  • the rotating part 400 is rotated in the reverse direction and the reverse gear G7 is in a non-rotating state, that is, the reverse gear G7 is connected to the rotating part 400 by the second one-way clutch bearing 122. Since the stepped state is rotated in the reverse direction together with the rotating unit 400, the turning gear G3 meshed with the reverse gear G7 rotates forward about the central axis of the third branch input link 103.
  • the output gear G3 in the non-rotating state engaged with the turning gear G8 receives the forward rotational force of the turning gear G8 and is centered on the rotational center axis X of the input link 100. It is rotated backwards.
  • only one second branch input link 102 in which the rotary part 400 is rotatably circumscribed is formed to protrude radially outwardly from one side of the input link 100.
  • the present invention is not limited thereto, and a plurality of protrusions may be formed in the radially outward direction with a predetermined interval in the circumferential direction of the input link 100.

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

Abstract

L'invention concerne une transmission à variation continue ayant une structure dans laquelle : on utilise un outil de manivelle à levier permettant d'établir un accouplement relié entre un organe d'entrée, une pluralité d'organes coupleurs et des organes de sortie qui sont au même nombre que les organes coupleurs; l'organe d'entrée effectue un mouvement de rotation; un axe variable permettant d'effectuer l'accouplement relié de l'organe d'entrée et de la pluralité d'organes coupleurs est disposé de manière excentrique depuis le centre de rotation de l'organe d'entrée, état dans lequel celui-ci est capable d'une variabilité élastique dans le sens radial du mouvement de rotation de l'organe d'entrée, en fonction d'une charge, tout en étant dans l'impossibilité d'effectuer des mouvements d'orbite et de rotation; un axe d'articulation, permettant d'effectuer l'accouplement relié de la pluralité d'organes coupleurs et de la pluralité d'organes de sortie, et une butée d'embrayage à roue libre sont intercalés de sorte qu'une pluralité de pignons de renvoi d'arbre primaire, qui entourent les arbres de sortie de la pluralité d'organes de sortie, orbitent autour d'un centre d'orbite qui est identique au centre de rotation de l'organe d'entrée; et un engrenage de sortie s'engrène avec la pluralité de pignons de renvoi d'arbre primaire, et ainsi la présente invention fait en sorte qu'il est structurellement facile d'assurer que l'axe variable qui est l'élément le plus important, c'est-à-dire l'axe variable effectuant l'accouplement relié de l'organe d'entrée et des organes coupleurs, est positionné de manière excentrique par rapport au centre de rotation de l'organe d'entrée.
PCT/KR2011/004233 2010-07-19 2011-06-09 Transmission à variation continue WO2012011662A2 (fr)

Applications Claiming Priority (10)

Application Number Priority Date Filing Date Title
KR1020100069498A KR101213546B1 (ko) 2010-07-19 2010-07-19 무단변속장치
KR10-2010-0069498 2010-07-19
KR1020100071334A KR101213547B1 (ko) 2010-07-23 2010-07-23 무단변속장치
KR10-2010-0071334 2010-07-23
KR10-2011-0031969 2011-04-07
KR1020110031968A KR101327336B1 (ko) 2011-04-07 2011-04-07 무단변속장치
KR1020110031969A KR101327332B1 (ko) 2011-04-07 2011-04-07 허브타입의 무단변속장치
KR10-2011-0031968 2011-04-07
KR1020110054798A KR101254596B1 (ko) 2011-06-07 2011-06-07 허브타입의 무단변속장치
KR10-2011-0054798 2011-06-07

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WO2012011662A2 true WO2012011662A2 (fr) 2012-01-26
WO2012011662A3 WO2012011662A3 (fr) 2012-05-03

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CN102937169A (zh) * 2012-11-15 2013-02-20 南京工程学院 永磁调速行星齿轮分流传动无级变速系统
CN102943850A (zh) * 2012-11-27 2013-02-27 邹政耀 永磁柔性锁定及控制无级变速系统
CN106785438A (zh) * 2017-01-26 2017-05-31 京信通信系统（中国）有限公司 传动装置及天线下倾角的控制系统
CN106785451A (zh) * 2017-01-26 2017-05-31 京信通信系统（中国）有限公司 天线及其下倾角控制装置
CN108502094A (zh) * 2018-05-14 2018-09-07 赵宁 行星齿轮无级变速系统
CN109723770A (zh) * 2017-10-31 2019-05-07 摩特动力工业股份有限公司 持续出力的无段变速器
CN109958744A (zh) * 2019-04-12 2019-07-02 苏州鼎智瑞光智能科技有限公司 一种脉动式无级变速器及其非圆齿轮的优化方法
CN110805673A (zh) * 2019-12-16 2020-02-18 哈尔滨理工大学 一种抗冲击的机械无级变速器
CN117772808A (zh) * 2024-02-23 2024-03-29 太原理工大学 一种校准异速比的齿轮装置及异步轧机

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CN102937169B (zh) * 2012-11-15 2015-05-06 南京工程学院 永磁调速行星齿轮分流传动无级变速系统
CN102937169A (zh) * 2012-11-15 2013-02-20 南京工程学院 永磁调速行星齿轮分流传动无级变速系统
CN102943850A (zh) * 2012-11-27 2013-02-27 邹政耀 永磁柔性锁定及控制无级变速系统
CN106785438B (zh) * 2017-01-26 2023-08-08 京信通信技术(广州)有限公司 传动装置及天线下倾角的控制系统
CN106785438A (zh) * 2017-01-26 2017-05-31 京信通信系统（中国）有限公司 传动装置及天线下倾角的控制系统
CN106785451A (zh) * 2017-01-26 2017-05-31 京信通信系统（中国）有限公司 天线及其下倾角控制装置
CN106785451B (zh) * 2017-01-26 2023-10-27 京信通信技术(广州)有限公司 天线及其下倾角控制装置
CN109723770A (zh) * 2017-10-31 2019-05-07 摩特动力工业股份有限公司 持续出力的无段变速器
CN108502094A (zh) * 2018-05-14 2018-09-07 赵宁 行星齿轮无级变速系统
CN108502094B (zh) * 2018-05-14 2024-04-02 赵宁 行星齿轮无级变速系统
CN109958744B (zh) * 2019-04-12 2021-08-03 苏州鼎智瑞光智能科技有限公司 一种脉动式无级变速器及其非圆齿轮的优化方法
CN109958744A (zh) * 2019-04-12 2019-07-02 苏州鼎智瑞光智能科技有限公司 一种脉动式无级变速器及其非圆齿轮的优化方法
CN110805673A (zh) * 2019-12-16 2020-02-18 哈尔滨理工大学 一种抗冲击的机械无级变速器
CN117772808A (zh) * 2024-02-23 2024-03-29 太原理工大学 一种校准异速比的齿轮装置及异步轧机
CN117772808B (zh) * 2024-02-23 2024-05-10 太原理工大学 一种校准异速比的齿轮装置及异步轧机

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