WO2017073993A1 - Transmission à variation continue - Google Patents

Transmission à variation continue Download PDF

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Publication number
WO2017073993A1
WO2017073993A1 PCT/KR2016/012040 KR2016012040W WO2017073993A1 WO 2017073993 A1 WO2017073993 A1 WO 2017073993A1 KR 2016012040 W KR2016012040 W KR 2016012040W WO 2017073993 A1 WO2017073993 A1 WO 2017073993A1
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WO
WIPO (PCT)
Prior art keywords
keys
pair
gear
drive
driven
Prior art date
Application number
PCT/KR2016/012040
Other languages
English (en)
Korean (ko)
Inventor
현경열
Original Assignee
현경열
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 KR1020150190643A external-priority patent/KR101745807B1/ko
Application filed by 현경열 filed Critical 현경열
Publication of WO2017073993A1 publication Critical patent/WO2017073993A1/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
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/06—Gearings for conveying rotary motion by endless flexible members with chains
    • 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
    • F16H9/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion
    • F16H9/24—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using chains or toothed belts, belts in the form of links; Chains or belts specially adapted to such gearing
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06K—GRAPHICAL DATA READING; PRESENTATION OF DATA; RECORD CARRIERS; HANDLING RECORD CARRIERS
    • G06K13/00—Conveying record carriers from one station to another, e.g. from stack to punching mechanism
    • G06K13/02—Conveying record carriers from one station to another, e.g. from stack to punching mechanism the record carrier having longitudinal dimension comparable with transverse dimension, e.g. punched card
    • G06K13/08—Feeding or discharging cards
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06K—GRAPHICAL DATA READING; PRESENTATION OF DATA; RECORD CARRIERS; HANDLING RECORD CARRIERS
    • G06K7/00—Methods or arrangements for sensing record carriers, e.g. for reading patterns
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01R—ELECTRICALLY-CONDUCTIVE CONNECTIONS; STRUCTURAL ASSOCIATIONS OF A PLURALITY OF MUTUALLY-INSULATED ELECTRICAL CONNECTING ELEMENTS; COUPLING DEVICES; CURRENT COLLECTORS
    • H01R12/00—Structural associations of a plurality of mutually-insulated electrical connecting elements, specially adapted for printed circuits, e.g. printed circuit boards [PCB], flat or ribbon cables, or like generally planar structures, e.g. terminal strips, terminal blocks; Coupling devices specially adapted for printed circuits, flat or ribbon cables, or like generally planar structures; Terminals specially adapted for contact with, or insertion into, printed circuits, flat or ribbon cables, or like generally planar structures
    • H01R12/70—Coupling devices
    • H01R12/71—Coupling devices for rigid printing circuits or like structures
    • H—ELECTRICITY
    • H04—ELECTRIC COMMUNICATION TECHNIQUE
    • H04B—TRANSMISSION
    • H04B1/00—Details of transmission systems, not covered by a single one of groups H04B3/00 - H04B13/00; Details of transmission systems not characterised by the medium used for transmission
    • H04B1/38—Transceivers, i.e. devices in which transmitter and receiver form a structural unit and in which at least one part is used for functions of transmitting and receiving
    • H04B1/3816—Mechanical arrangements for accommodating identification devices, e.g. cards or chips; with connectors for programming identification devices

Definitions

  • the present invention relates to a continuously variable transmission, and more particularly, to a continuously variable transmission in which an adjustment structure of a transmission range is improved.
  • Transmissions used in automobiles are classified into manual transmissions and automatic transmissions according to the transmission method, and automatic transmissions are classified into a stepped automatic transmission and a continuously variable transmission (CVT).
  • CVT continuously variable transmission
  • the transmission enables idling of the engine when the vehicle is stopped and enables the reverse by changing the rotational direction of the driving wheel.
  • the transmission ratio according to the rotational speed of the engine is extremely limited, and thus a shift stage is present because a shift stage is made between certain transmission ranges.
  • all transmission ratios within a given range can be selected continuously. Therefore, in a vehicle equipped with the continuously variable transmission, the transmission ratio for driving conditions is implemented so that the engine is operated at the required rotational driving point. It becomes possible.
  • a method of continuously changing speed is adopted by changing the effective diameter of a pulley using a rubber belt.
  • the speed ratio is changed steplessly by changing the width of both pulleys, and the width of each pulley is adjusted mainly by hydraulic pressure.
  • the effective diameter of the drive pulley is small, the effective diameter of the driven pulley is increased to obtain a low speed shift stage.
  • the effective diameter of the driven pulley decreases, the high speed shift stage can be obtained. have.
  • the conventional continuously variable transmission is variable in diameter while the variable side pulley of the primary pulley is moved left and right by hydraulic pressure, and thus the secondary pulley is different from the primary pulley while supporting the variable side pulley by the elastic force of the spring. Relative variable operation is made. Then, power is transmitted while shifting by a belt connected to the variable-controlled primary pulley and the secondary pulley.
  • the conventional continuously variable transmission controls the transmission ratio while the diameter of the pulley is variable in accordance with the supply of hydraulic pressure, so a separate hydraulic device is required, and the transmission is enlarged in size, and the power is transmitted by the belt. There is a problem that slip occurs between the power transmission efficiency is lowered.
  • the present invention has been made in view of the above, and according to the present invention, it is an object of the present invention to provide a continuously variable transmission in which the size of the transmission is made compact and the power transmission efficiency can be improved.
  • the drive shaft A drive gear provided to be movable on the drive shaft and formed of a conical gear in which a plurality of first key grooves are formed in a radial direction along an inclined surface; A plurality of first keys parallel to the drive shaft and partially protruding from the inclined surface of the drive gear, and movably coupled to the plurality of first key grooves, respectively; Driven shaft; A driven gear provided to be movable on the driven shaft, the driven gear comprising a conical gear having a plurality of second key grooves in a radial direction along an inclined surface; A plurality of second keys parallel to the driven shaft and partially protruding from the inclined surface of the driven gear, and movably coupled to the plurality of second key grooves, respectively; A power transmission member interconnecting the drive gear and the driven gear through the plurality of first keys and the plurality of second keys, and transmitting a rotational force of the drive gear to the driven gear; And a speed change control unit configured to adjust the rotation radius of the
  • a continuously variable transmission may include a shift control unit configured to increase or decrease an increase or decrease an increase or
  • the size of the transmission can be made compact, and the power transmission efficiency can be improved.
  • FIG. 1 is a perspective view of a continuously variable transmission according to an embodiment of the present invention.
  • FIG. 2 is a perspective view of a holder and a screw shaft removed in FIG. 1;
  • FIG. 3 is a perspective view of a state in which the power transmission member is removed in FIG.
  • FIG. 4 is a perspective view of a state in which each guide is removed from FIG.
  • Figure 5 is a perspective view of one power transmission member assembled in Figure 4.
  • FIG. 6 is a perspective view of a main first key and a main second key in FIG. 4;
  • FIG. 7 is a perspective view of an auxiliary first key and an auxiliary second key in FIG. 4; FIG.
  • FIG. 8 is a perspective view of each guide in FIG.
  • FIG. 9 is a perspective view of the holder in FIG. 1;
  • FIG. 10 is a perspective view of a continuously variable transmission according to another embodiment of the present invention.
  • FIG. 11 is a perspective view of a state in which the drive motor is removed in FIG.
  • FIG. 12 is a perspective view of a state in which some gears are removed from FIG. 11; FIG.
  • FIG. 13 is a perspective view of a state in which the screw shaft drive unit is removed in FIG.
  • FIG. 14 is a perspective view of a state in which each guide plate is removed in FIG. 13.
  • FIG. 15 is a perspective view of a state in which the power transmission member is removed in FIG.
  • FIG. 16 is a perspective view illustrating a coupling state of a driving shaft and a driving gear or a driven shaft and a driven gear in FIG. 15;
  • FIG. 17 is an explanatory diagram for explaining a speed increase process in FIG. 14;
  • Figure 18 is a perspective view of the main portion of the power transmission member commonly applied to various embodiments of the present invention.
  • 19 is an exploded state diagram for explaining a coupling relationship between each key formed on a driving gear side and a power transmission member in various embodiments of the present disclosure.
  • 20 is a view illustrating a coupling state of a ratchet and a main first key and a ratchet and a main second key commonly applied to various embodiments of the present disclosure.
  • 1 to 9 illustrate a continuously variable transmission according to an embodiment of the present invention.
  • the continuously variable transmission 1 includes a drive shaft 11, a drive gear 21 having a conical structure, a plurality of first keys 31, and a driven shaft 51. , A driven gear 61 having a conical structure, a plurality of second keys 71, a power transmission member 91, and a shift control unit 101.
  • the drive shaft 11 receives power for driving.
  • the input power is output through the driven shaft 51 after being added or subtracted by the structure to be described later. Acceleration may include both speed and torque.
  • a spline key 13 is formed in the drive shaft 11 so that the drive gear 21 is splined.
  • the drive gear 21 is formed with a boss 23 through which the drive shaft 11 is penetrated.
  • Spline grooves 23a which are splined to the spline key 13 of the drive shaft 11 are formed in the inner circumference of the boss 23.
  • an inclined surface 25 that forms an inclination along the circumference of the boss 23 is formed at one side of the drive gear 21.
  • the inclined surface 25 of the drive gear 21 is formed with a plurality of first key grooves 27 recessed in the radial direction along the inclined surface 25.
  • a plurality of first fitting protrusions 29 are formed to protrude from the plurality of first key grooves 27, and each of the first fitting protrusions 29 has an inclination angle of the inclined surface 25 of the drive gear 21.
  • Has The plurality of first key grooves 27 are recessed from the inclined surface 25 of the drive gear 21 to the outer circumference of the boss 23.
  • the plurality of first keys 31 have a block shape having a predetermined length and are movable in the plurality of first key grooves 27 to be parallel to the driving shaft 11 and to partially protrude from the inclined surface 25 of the drive gear 21. To be combined.
  • the plurality of first keys 31 are guide grooves for guiding sliding of the wedge groove 37 and the ratchet 97 to which the ratchet 97 of the power transmission member 91 to be described later engages.
  • a plurality of main first keys 33 formed at intervals 39 and a pair of guide grooves 39 for guiding sliding of the ratchet 97 as shown in FIG. 7 are formed at intervals.
  • Auxiliary first key 35 is included.
  • the wedge groove 37 and the guide groove 39 of the first key 31 the wedge groove 37 has a trapezoidal cross-sectional shape in close contact with the ratchet 97, as shown in FIG.
  • the groove 39 has a rectangular cross-sectional shape having a clearance with the ratchet 97.
  • first fitting grooves 41 fitted to first fitting protrusions 29 of the first key grooves 27 on both side surfaces of the plurality of main first keys 33 and the plurality of auxiliary first keys 35. Each of these recesses is formed.
  • the bottom surface of the wedge groove 37 and the guide groove 39 of the first key 31 interferes with the inclined surface 25 of the drive gear 21 by the ratchet 97 of the power transmission member 91. In order to prevent this from happening, it is spaced apart from the inclined surface 25 of the drive gear 21.
  • the first fitting protrusion 29 protrudes from the first key groove 27, and the first fitting protrusion is formed on the plurality of main first keys 33 and the plurality of auxiliary first keys 35.
  • the first fitting grooves 41 to be fitted into the 29 are shown as being recessed, but not limited thereto, the first keying grooves 27 are recessed and formed in the first key grooves 27.
  • the first fitting protrusion 29 may be formed to protrude from the main first key 33 and the plurality of auxiliary first keys 35 to be fitted to the first fitting groove 41.
  • a plurality of main first keys 33 and a plurality of auxiliary first keys 35 may include a plurality of first key grooves 27 of the drive gear 21. Are alternately mounted along the circumference of the drive shaft 11.
  • each of the wedge grooves 37 of the pair of main first keys 33 disposed with the auxiliary first key 35 therebetween moves in the direction of movement of the power transmission member 91.
  • the plurality of first keys 31 coupled to the plurality of first key grooves 27 of the drive gear 21 are spaced apart from the vertex area of the drive gear 21, the plurality of first keys 31 The radius of rotation becomes large.
  • the rotation of the plurality of first keys 31 is performed. The radius becomes smaller.
  • the main first key 33 and the auxiliary first key 35 are alternately mounted on the drive gear 21, a plurality of agents coupled to each of the first key grooves 27 of the drive gear 21 are provided.
  • the driven shaft 51 is spaced apart in parallel with the drive shaft 11, and outputs the power input from the drive shaft 11.
  • the spline key 53 is formed in the driven shaft 51 so that the driven gear 61 may spline-couple.
  • the driven gear 61 has the same shape and size as the drive gear 21, and as shown in FIG. 4, the driven shaft 51 so that the vertex area is disposed in a direction opposite to the vertex area of the drive gear 21. Is coupled to move.
  • the driven gear 61 is formed with a boss 63 through which the driven shaft 51 is coupled in the center.
  • On the inner circumference of the boss 63 is formed a spline groove 63a which is splined to the spline key 53 of the driven shaft 51.
  • one side of the driven gear 61 is formed with an inclined surface 65 inclined along the circumference of the boss (63).
  • a plurality of second key grooves 67 are recessed in the radial direction along the inclined surface 65.
  • a plurality of second fitting protrusions 69 protruding from each other are formed in the plurality of second key grooves 67, and each second fitting protrusion 69 has an inclination angle of the inclined surface 65 of the driven gear 61.
  • Has The plurality of second key grooves 67 are recessed from the inclined surface 65 of the driven gear 61 to the outer circumference of the boss 63.
  • the plurality of second keys 71 have a block shape of a predetermined length, and move in the plurality of second key grooves 67 to be parallel to the driven shaft 51 and to partially protrude from the inclined surface 65 of the driven gear 61. Possibly combined.
  • the plurality of second keys 71 are guide grooves 79 for guiding sliding of the ratchet 97 and the wedge groove 77 to which the ratchet 97 of the power transmission member 91 is engaged.
  • the wedge groove 77 and the guide groove 79 of the second key 71 are the same as the wedge groove 37 and the guide groove 39 of the first key. It has a trapezoidal cross-sectional shape in close contact, and the guide groove 79 has a rectangular cross-sectional shape having a clearance with the ratchet 97.
  • second fitting grooves 81 fitted to the second fitting protrusions 69 of the second key grooves 67 on both side surfaces of the plurality of main second keys 73 and the plurality of auxiliary second keys 75. Each of these recesses is formed.
  • the bottom surface of the wedge groove 77 and the guide groove 79 of the second key 71 has the ratchet 97 of the power transmission member 91 interfering with the inclined surface 65 of the driven gear 61. In order not to generate
  • the second fitting protrusion 69 is formed to protrude in the second key groove 67, and the second to the plurality of main second keys 73 and the plurality of auxiliary second keys 75 are second.
  • the second fitting grooves 81 fitted to the fitting protrusions 69 are shown as being recessed, respectively, but are not limited thereto, the second fitting grooves 81 may be recessed in the second key groove 67.
  • the second fitting protrusions 69 fitted into the second fitting grooves 81 may be formed in the plurality of main second keys 73 and the auxiliary second keys 75, respectively.
  • the main second key 73 has the same shape and size as the main first key 33
  • the auxiliary second key 75 preferably has the same shape and size as the auxiliary first key 35. .
  • a plurality of main second keys 73 and a plurality of auxiliary second keys 75 may include a plurality of second key grooves 67 of the driven gear 61. Are alternately mounted along the circumference of the driven shaft 51. Further, in the same structure as that of the drive gear 21 side (Fig. 19), each of the wedge grooves 77 of the pair of main second keys 73 disposed with the auxiliary second key 75 therebetween is power transmission.
  • the members 91 are alternately arranged alternately with respect to the moving direction of the member 91.
  • the plurality of second keys 71 coupled to the plurality of second key grooves 67 of the driven gear 61 are spaced apart from the vertex region of the driven gear 61, the plurality of second keys 71 The radius of rotation becomes large.
  • the rotation of the plurality of second keys 71 is performed. The radius becomes smaller.
  • a plurality of agents coupled to each second key groove 67 of the driven gear 61 is stably engaged without departing from the wedge groove 77 of the second key 71.
  • the power transmission member 91 as shown in Figure 18, a plurality of connecting links 93 having a predetermined length is connected by a pin 95 to form a closed loop shape, at the same time, a plurality of connections
  • the link 93 has the shape of a chain conveyor arranged at intervals transversely with respect to the moving direction of the power transmission member 91.
  • a plurality of ratchets 97 are coupled to the power transmission member 91 as attachments, and the plurality of ratchets 97 are arranged at regular intervals along the moving direction of the power transmission member 91.
  • the ratchet 97 is engaged with the wedge grooves 37 and 77 formed in the plurality of first keys 31 and the plurality of second keys 71 or slides into the guide grooves 39 and 79.
  • the power transmission member 91 interconnects the drive gear 21 and the driven gear 61 through the plurality of first keys 31 and the plurality of second keys 71, The rotational force is transmitted to the driven gear 61.
  • a pair of power transmission members (91a, 91b) are arranged in parallel so as to be able to rotate independently of each other.
  • each ratchet 97 of the pair of power transmission members 91a and 91b is connected to the first key 31.
  • the wedge groove 37 and the second key 71 of the wedge groove 77 of each of them without departing from the stable engagement, it is possible to continuously transmit power.
  • each of the wedge grooves 37 of the pair of main first keys 33 disposed with the auxiliary first key 35 therebetween is connected to the pair of power transmission members 91a and 91b.
  • Each pair of wedge grooves 77 of a pair of main second keys 73 arranged alternately laterally alternately with respect to the movement direction and arranged with the auxiliary second key 75 interposed therebetween is a pair of power transmission.
  • a pair of power transmission members is disposed when the rotation radius of the plurality of first keys 31 and the plurality of second keys 71 is changed by alternately shifting horizontally with respect to the moving directions of the members 91a and 91b.
  • each ratchet 97 of one side power transmission member 91a has a wedge groove of first key 31 disposed along the moving direction of one side power transmission member 91a. 37) and stably engages without deviating from the wedge grooves 77 of the second key 71, respectively, and can continuously transmit power, and the other power transmission unit
  • Each ratchet 97 of the ash 91b has a wedge groove 37 of the first key 31 and a wedge groove 77 of the second key 71 arranged along the direction of movement of the other power transmission member 91b. It is possible to reliably engage and transmit power continuously without deviating from each other.
  • the rotation radius of the plurality of first keys 31 coupled to the drive gear 21 and the rotation radius of the plurality of second keys 71 coupled to the driven gear 61 are increased or decreased in opposite directions. Adjust to That is, in the shift control unit 101, as the vertex regions of the drive gear 21 and the driven gear 61 are arranged in opposite directions, the plurality of first keys 31 and the plurality of second keys 71 are arranged.
  • the rotation radius of the first key 31 decreases and the rotation radius of the second key 71 increases, and conversely, the plurality of first keys 31 and the plurality of By simultaneously moving the second key 71 to the vertex area of the driven gear 61, the rotation radius of the first key 31 increases and the rotation radius of the second key 71 decreases. Therefore, the rotation speeds of the plurality of first keys 31 and the plurality of second keys 71 are changed to adjust the speed change.
  • the shift control unit 101 includes a pair of first guides 103, a pair of second guides 107, a pair of holders 111, a screw shaft 121, and a screw shaft driver 125. ).
  • the pair of first guides 103 are reciprocally coupled to the drive gear 21 with a plurality of first keys 31 coupled to the plurality of first key grooves 27 interposed therebetween.
  • Each first guide 103 is provided with a first pusher 105 which is inserted into a plurality of first key grooves 27 and presses both ends of the first key 31 as shown in FIG. 8.
  • the pair of second guides 107 are reciprocally coupled to the driven gear 61 with a plurality of second keys 71 coupled to the plurality of second key grooves 67 interposed therebetween.
  • Each second guide 107 is provided with a second pusher 109 inserted into the plurality of second key grooves 67 and pressing both ends of the second key 71 as shown in FIG. 8.
  • the pair of holders 111 are interconnected at intervals by brackets 117 as shown in FIG. 9, and the pair of first guides 103 and the pair of second guides 107 are thrust bearings. And rotatably supported by 113.
  • a screw portion 115 is provided in the center of each holder 111, and the screw portion 115 has a screw penetratingly formed in parallel with the drive shaft 11.
  • the pair of holders 111 are supported by a structure such as a frame by a support 119 coupled to the bracket 117.
  • the screw shaft 121 has a rod shape having a predetermined length having a screw formed on an outer circumference thereof, and is screwed to the threaded portion 115 of the holder 111 to linearly move the holder 111.
  • the screw shaft 121 is rotated in the forward direction, the holder 111 moves in the direction of the vertex region of the drive gear 21, and the pushers 105 and 109 of the first guide 103 and the second guide 107 are moved.
  • One end of the first key 31 and the second key 71 is pressed by the first key 31 and moves in the direction of the vertex area of the drive gear 21, so that the rotation radius of the first key 31 decreases and the second key 71 The rotation radius is increased, so that the continuously variable transmission 1 according to the embodiment of the present invention is decelerated.
  • the screw shaft driver 125 is connected to the screw shaft 121 to rotate the screw shaft 121 forward and backward.
  • the motor directly connected to the screw shaft 121 is shown as the screw shaft driver 125, the present invention is not limited thereto.
  • the screw shaft driver is coupled to the motor, the screw shaft 121, and the motor shaft, respectively. It can be made of a sprocket of the chain, connecting a pair of sprockets and transmitting power.
  • the first key 31 coupled to the first key groove 27 of the drive gear 21 is positioned at the center of the drive gear 21 and the second key coupled to the second key groove 67 of the driven gear 61.
  • the rotation radius of the first key 31 coupled to the first key groove 27 of the drive gear 21 and the second key groove of the driven gear 61 are shown.
  • the rotation radius of the second key 71 coupled to the 67 is the same, so that a shift does not occur between the drive gear 21 and the driven gear 61.
  • the power input through the drive shaft 11 is driven by the drive gear 21, the plurality of first keys 31, the power transmission member 91, the plurality of second keys 71, and the driven gear ( 61 is sequentially passed through the driven shaft (51). At this time, a shift does not occur between the drive gear 21 and the driven gear 61, and the drive shaft 11 and the driven shaft 51 rotate at the same rotational speed.
  • the holder 111 In the state where the rotation radius of the first key 31 of the drive gear 21 and the rotation radius of the second key 71 of the driven gear 61 are the same, the holder 111 is in the vertex region direction of the driven gear 61. Rotate the screw shaft 121 in the reverse direction to move to.
  • the other ends of the first key 31 and the second key 71 are formed by the pushers 105 and 109 of the first guide 103 and the second guide 107. Pressurized and moved together in the direction of the vertex region of the driven gear 61, the first key 31 coupled to the first key groove 27 of the driven gear 61 is increased in the radius of rotation, and of the driven gear 61 The radius of rotation of the second key 71 coupled to the second key groove 67 is reduced.
  • the rotation radius of the plurality of first keys 31 coupled to the drive gear 21 is adjusted by the shift adjustment unit 101 to the plurality of second keys 71 coupled to the driven gear 61.
  • the speed increase occurs by a ratio of the rotation radius of the plurality of first keys 31 and the rotation radius of the plurality of second keys 71.
  • the power input through the drive shaft 11 is driven by the drive gear 21, the plurality of first keys 31, the power transmission member 91, the plurality of second keys 71, and a pair of pairs.
  • the driven gear 61 is sequentially transmitted through the driven shaft 51.
  • an increase in speed is generated by a ratio of the rotation radius of the plurality of first keys 31 and the rotation radius of the plurality of second keys 71.
  • 51 rotates with the rotation speed which speeded up with respect to the drive shaft 11. As shown in FIG.
  • the holder 111 In the state where the rotation radius of the first key 31 of the drive gear 21 and the rotation radius of the second key 71 of the driven gear 61 are the same, the holder 111 is in the vertex region direction of the drive gear 21. Rotate the screw shaft 121 in the forward direction to move to.
  • the rotation radius of the plurality of first keys 31 coupled to the drive gear 21 is adjusted by the shift adjustment unit 101 to the plurality of second keys 71 coupled to the driven gear 61.
  • deceleration occurs by the ratio of the rotation radius of the plurality of first keys 31 and the rotation radius of the plurality of second keys 71.
  • the power input through the drive shaft 11 is driven by the drive gear 21, the plurality of first keys 31, the power transmission member 91, the plurality of second keys 71, and a pair of pairs.
  • the driven gear 61 is sequentially transmitted through the driven shaft 51.
  • deceleration is generated by the ratio of the rotation radius of the plurality of first keys 31 and the rotation radius of the plurality of second keys 71, and the driven shaft 51 rotates with the rotation speed decelerated with respect to the drive shaft 11. As shown in FIG.
  • the continuously variable transmission 2 includes a drive shaft 211, a drive gear 220 formed of a pair of conical gears 221, and a plurality of first keys ( 231, a driven shaft 241, a driven gear 250 formed of a pair of conical gears 251, a plurality of second keys 261, a power transmission member 271, and a shift control unit 281. do.
  • the drive shaft 211 receives power for driving.
  • the input power is output through the driven shaft 241 after being added or subtracted by a structure to be described later. Acceleration may include both speed and torque.
  • the drive shaft 211 is formed with a spline key 213 so that the drive gear 221 is splined.
  • Conical gears 221 forming the drive gear 220 are formed in the same structure with each other, as shown in Figure 16, the spline groove 223 is splined to the spline key 213 of the drive shaft 211 in the center Is formed, the inclined surface 225 is formed on one side inclined along the circumference of the spline groove 223.
  • the conical gears 221 are coupled to the drive shaft 211 so that each inclined surface 225 opposes each other and are spaced apart from each other.
  • the inclined surface 225 of the conical gear 221 is formed with a plurality of first key grooves 227 recessed to a predetermined depth in the radial direction along the inclined surface 225.
  • the plurality of first keys 231 have a bar shape having a predetermined length and are provided between the pair of conical gears 221 to interconnect the pair of conical gears 221. In this case, the plurality of first keys 231 are movably engaged with the first key grooves 227 at positions corresponding to each other of the driving gear 220.
  • the plurality of first keys 231 move along the radial direction of the drive shaft 211, that is, along the radial direction of the drive gear 220.
  • the plurality of first keys 231 move along the plurality of first key grooves 227 in a direction away from the drive shaft 211, and thus, the plurality of first keys.
  • the radius of rotation of 231 becomes large.
  • the plurality of first keys 231 move along the plurality of first key grooves 227 toward the driving shaft 211, and thus, the plurality of first keys 231 The radius of rotation becomes smaller.
  • the plurality of first keys 231 are spaced between the wedge groove 237 to which the ratchet 277 of the power transmission member 271 to be described later engages, and the guide groove 239 for guiding the sliding of the ratchet 277.
  • the plurality of main first keys 233 and the pair of guide grooves 239 for guiding the sliding of the ratchet 277 include a plurality of auxiliary first keys 235 formed at intervals.
  • the wedge groove 237 of the first key 231 has a trapezoidal cross-sectional shape in close contact with the ratchet 277, and the guide groove 239 of the first key 231 has a square having a clearance with the ratchet 277. In the cross-sectional shape of, as shown in FIG. 10, the same shape as that of one embodiment of the present invention may be taken.
  • a plurality of main first keys 233 and a plurality of auxiliary first keys 235 may include a plurality of first key grooves 227 of the drive gear 220. Are alternately mounted along the circumference of the drive shaft 211.
  • each of the wedge grooves 237 of the pair of main first keys 233 disposed with the auxiliary first key 235 therebetween moves in the direction of movement of the power transmission member 271.
  • the radius of rotation of the plurality of first keys 231 formed on the drive gear 220 is changed.
  • the ratchet 277 of the power transmission member 271 is stably engaged without departing from the wedge groove 237 of the first key 231.
  • the driven shaft 241 is spaced apart in parallel with the drive shaft 211 and outputs power input from the drive shaft 211.
  • a spline key 243 is formed on the driven shaft 241 so that the pair of conical gears 251 forming the driven gear 250 are splined together.
  • the pair of conical gears 251 forming the driven gear 250 are formed in the same structure, and as shown in FIG. 16, a spline splined to the spline key 243 of the driven shaft 241 at the center thereof.
  • the groove 253 is formed.
  • the inclined surface 255 is formed on one side inclined along the circumference of the spline groove 253.
  • the pair of conical gears 251 are coupled to the driven shaft 241 so that each of the inclined surfaces 255 face each other, so as to approach or be spaced apart from each other.
  • the inclined surface 255 of each conical gear 251 is formed with a plurality of second key grooves 257 recessed in a radial direction along the inclined surface 255 to a predetermined depth.
  • the driven gear 250 has the same shape and size as the drive gear 220.
  • the plurality of second keys 261 have a bar shape having a predetermined length, and are connected to a pair of conical gears 251 provided on the driven gear 250 to form the driven gear 250.
  • the plurality of second keys 261 are movably engaged with the second key grooves 257 at positions corresponding to the driven gears 250.
  • the second key 261 preferably has the same shape and size as the first key 231.
  • the plurality of second keys 261 are moved along the radial direction of the driven shaft 241, that is, along the radial direction of the driven gear 250.
  • the plurality of second keys 261 connecting between the pair of conical gears 251 are driven along the plurality of second key grooves 257.
  • the rotational radius of the plurality of second keys 261 is increased by moving in the direction away from the second key 261.
  • the plurality of second keys 261 move along the plurality of second key grooves 257 toward the driven shaft 241, and thus the plurality of second keys 261.
  • the radius of rotation becomes smaller.
  • the plurality of second keys 261 are formed at intervals between the wedge groove 267 to which the ratchet 277 of the power transmission member 271 engages and the guide groove 269 for guiding the sliding of the ratchet 277.
  • the plurality of main second keys 263 and the pair of guide grooves 269 for guiding the sliding of the ratchet 277 include a plurality of auxiliary second keys 265 spaced apart from each other.
  • the wedge groove 267 of the second key 261 has a trapezoidal cross-sectional shape in close contact with the ratchet 277, and the guide groove 269 of the second key 261 has a square having a clearance with the ratchet 277. In cross-sectional shape. As shown in FIG. 10, the shape may be the same as that of the exemplary embodiment of the present invention.
  • a plurality of main second keys 263 and a plurality of auxiliary second keys 265 may include a plurality of second key grooves 257 of the driven gear 250. Are alternately mounted along the circumference of the driven shaft 241. Further, the wedge grooves 267 of the pair of main second keys 263 disposed with the auxiliary second key 265 interposed therebetween in the same structure as the drive gear 221 side (Fig. 19) are the power transmission member. It is alternately shifted laterally with respect to the moving direction of 271.
  • the rotation of the plurality of second keys 261 mounted on the driven gear 250 is performed.
  • the ratchet 277 of the power transmission member 271 is stably engaged without departing from the wedge groove 267 of the second key 261.
  • the power transmission member 271 is formed in the same structure as the power transmission member 91 applied in one embodiment of the present invention, and as shown in FIG. 18, the plurality of connection links 273 having a predetermined length include a pin 275.
  • a plurality of connecting links (273) has a shape of a chain conveyor arranged at intervals horizontally with respect to the moving direction of the power transmission member (271).
  • a plurality of ratchets 277 are coupled to the power transmission member 271 as attachments, and as illustrated in FIG. 9, the plurality of ratchets 277 are disposed at regular intervals along the moving direction of the power transmission member 271.
  • the power transmission member 271 is arranged horizontally with respect to the moving direction.
  • the ratchet 277 is engaged with the wedge grooves 237 and 267 formed in the plurality of first keys 231 and the plurality of second keys 261 or slidable to the guide grooves 239 and 269.
  • the power transmission member 271 interconnects the drive gear 220 and the driven gear 250 through the plurality of first keys 231 and the plurality of second keys 261. The rotational force is transmitted to the driven gear 250.
  • the shift adjusting unit 281 adjusts the gap between the drive gear 220 and the gap between the driven gear 250 to increase and decrease in opposite directions. That is, in the shift control unit 281, the plurality of first keys 231 and the plurality of second keys 261 are opposite to each other along the plurality of first key grooves 227 and the plurality of second key grooves 257, respectively. Direction, for example, by changing each rotation radius of the plurality of first keys 231 and the plurality of second keys 261 to adjust the shift.
  • the shift control unit 281 includes a pair of drive screw shafts 283, a pair of driven screw shafts 285, a pair of first guide plates 287, and a pair of second guide plates 291. ) And a screw shaft drive unit 301.
  • the pair of driving screw shafts 283 are formed in parallel with the driving shaft 211 and provided with the driving gear 220 interposed therebetween. Both ends of the pair of drive screw shafts 283 are provided with screws in mutually different thread directions, and a pair of first guide plates 287 are screwed to these screws.
  • the pair of driven screw shafts 285 are in parallel with the driven shaft 241, and are provided with the driven gear 250 interposed therebetween. Both ends of the pair of driven screw shafts 285 are provided with screws in mutually different thread directions, and a pair of second guide plates 291 are screwed to these screws.
  • the pair of first guide plates 287 are provided with the drive gear 220 interposed therebetween, and the pair of drive screw shafts 283 are screwed together while the drive shaft 211 is penetrated and defective. As shown in FIG. 4, the first guide plate 287 is provided with a pair of screw holes 289 in which a pair of drive screw shafts 283 are screwed together.
  • the pair of second guide plates 291 are provided with the driven gear 250 interposed therebetween, while the driven shaft 241 penetrates through defects, and the pair of driven screw shafts 285 are each screwed together.
  • the second guide plate 291 is formed with a pair of screw holes 293 in which a pair of driven screw shafts 285 are screwed together.
  • the screw shaft driver 301 adjusts the distance of the drive gear 220 by a pair of first guide plates 287, and is driven opposite to the drive gear 220 by a pair of second guide plates 291.
  • the pair of drive screw shafts 283 and the pair of driven screw shafts 285 are rotated so that the distance between the gears 250 is adjusted.
  • the screw shaft drive unit 301 includes a drive motor 303, a drive motor gear 305, a first gear 307, a pair of drive sprockets 309, a drive chain 311, and a second gear. 315, a pair of driven sprockets 317, and a driven chain 319.
  • the drive motor gear 305 has a form of an outer tooth in which a plurality of gear teeth are formed, and is coupled to an axis of the drive motor 303 to rotate by the rotation of the drive motor 303.
  • the first gear 307 has the form of an external tooth having the same gear tooth size as that of the drive motor gear 305, and is coupled to any one of the pair of drive screw shafts 283, so as to be coupled to the drive motor gear 305. Rotate to interlock.
  • the first gear 307 has a larger diameter than the drive motor gear 305.
  • the pair of drive sprockets 309 are respectively coupled to one end of the pair of drive screw shafts 283.
  • the drive chain 311 connects a pair of drive sprockets 309 and transmits power between the pair of drive sprockets 309.
  • the second gear 315 has the form of an external tooth having the same gear tooth size as the first gear 307, and is coupled to any one of the pair of driven screw shafts 285, so as to be coupled to the first gear 307. Rotate to interlock.
  • the second gear 315 has the same diameter as the first gear 307. As a result, the second gear 315 and the first gear 307 rotate at the same rotational speed.
  • the pair of driven sprockets 317 are respectively coupled to one end of the pair of driven screw shafts 285.
  • the driven chain 319 connects a pair of driven sprockets 317 and transmits power between the pair of driven sprockets 317.
  • the rotation radius of the 231 and the rotation radius of the plurality of second keys 261 mounted on the driven gear 250 are the same, so that a shift does not occur between the drive gear 220 and the driven gear 250.
  • the power input through the drive shaft 211 is driven by the drive gear 220, the plurality of first keys 231, the power transmission member 271, the plurality of second keys 261, and the driven gear ( 250 is sequentially passed through the driven shaft 241.
  • the shift does not occur between the drive gear 220 and the driven gear 250, the drive shaft 211 and the driven shaft 241 is rotated at the same rotational speed.
  • the rotational force of the drive motor 303 is transmitted to the drive motor gear 305, a part of the rotational force of the drive motor 303 is transmitted to the first gear 307, the rest of the rotational force of the drive motor 303 is the first It is transmitted to the second gear 315 which rotates in engagement with the gear 307.
  • the rotational force of the drive motor 303 transmitted to the first gear 307 is transmitted to the pair of drive sprockets 309 and the drive chain 311 to rotate the pair of drive screw shafts 283 in the same direction.
  • the drive motor 303 and the first gear 307 is rotated in the opposite direction, and at the same time a pair of drive screw shaft 283 also rotates in the opposite direction to the drive motor 303.
  • the pair of drive screw shafts 283 rotate in the opposite direction to the drive motor 303, the pair of first guide plates 287 screwed with the pair of drive screw shafts 283 is one By the screw movement with the pair of drive screw shafts 283 are mutually approached, the distance between the drive gear 220 is reduced.
  • the plurality of first keys 231 mounted on the drive gear 220 are moved along the plurality of first key grooves 227 in a direction away from the drive shaft 211, thereby driving the drive gear 220.
  • the rotation radius of the plurality of mounted first keys 231 is relatively larger than when the shift is not performed.
  • the remaining rotational force of the drive motor 303 transmitted to the second gear 315 is transmitted to the pair of driven sprockets 317 and the driven chain 319 to move the pair of driven screw shafts 285 in the same direction.
  • the driving motor 303 and the second gear 315 rotate in the same direction, and at the same time, the pair of driven screw shafts 285 also rotate in the same direction with the driving motor 303.
  • the pair of driven screw shafts 285 rotates in the same direction as the drive motor 303, the pair of second guide plates 291 screwed with the pair of driven screw shafts 285 become one.
  • the plurality of second keys 261 mounted on the driven gear 250 are moved toward the driven shaft 241 along the plurality of second key grooves 257, whereby the plurality of second keys 261 are mounted on the driven gear 250.
  • the rotation radius of the plurality of second keys 261 becomes relatively smaller than when the shift is not performed.
  • the rotation radius of the plurality of first keys 231 mounted on the drive gear 220 is adjusted by the shift adjustment unit 281 of the plurality of second keys 261 mounted on the driven gear 250.
  • the speed increase occurs by a ratio of the rotation radius of the plurality of first keys 231 and the rotation radius of the plurality of second keys 261.
  • the power input through the drive shaft 211 is driven by the drive gear 220, the plurality of first keys 231, the power transmission member 271, the plurality of second keys 261, and the driven gear ( 250 is sequentially passed through the driven shaft 241.
  • the speed is increased by the ratio of the rotation radius of the plurality of first keys 231 and the rotation radius of the plurality of second keys 261, the driven shaft 241 is rotated at an increased speed with respect to the drive shaft 211.
  • the drive motor 303 is increased so that the distance between the drive gear 220 is increased. Rotate in the other direction.
  • the rotational force of the drive motor 303 is transmitted to the drive motor gear 305, a part of the rotational force of the drive motor 303 is transmitted to the first gear 307, the rest of the rotational force of the drive motor 303 is the first It is transmitted to the second gear 315 which rotates in engagement with the gear 307.
  • the rotational force of the drive motor 303 transmitted to the first gear 307 is transmitted to the pair of drive sprockets 309 and the drive chain 311 to rotate the pair of drive screw shafts 283 in the same direction.
  • the drive motor 303 and the first gear 307 is rotated in the opposite direction, and at the same time a pair of drive screw shaft 283 also rotates in the opposite direction to the drive motor 303.
  • the pair of first guide plates 287 screwed with the pair of drive screw shafts 283 is one They are spaced apart from each other by a screw movement with the pair of drive screw shafts 283, thereby increasing the distance of the drive gear 220.
  • the plurality of first keys 231 mounted on the drive gear 220 are moved toward the drive shaft 211 along the plurality of first key grooves 227, whereby the plurality of first keys 231 are mounted on the drive gear 220.
  • Rotation radius of the first key 231 is relatively smaller than when the shift does not occur.
  • the remaining rotational force of the drive motor 303 transmitted to the second gear 315 is transmitted to the pair of driven sprockets 2117 and the driven chain 319 to move the pair of driven screw shafts 285 in the same direction.
  • the driving motor 303 and the second gear 315 rotate in the same direction, and at the same time, the pair of driven screw shafts 285 also rotate in the same direction with the driving motor 303.
  • the pair of driven screw shafts 285 rotates in the same direction as the drive motor 303, the pair of second guide plates 291 screwed with the pair of driven screw shafts 285 become one.
  • the pair of driven screw shafts 285 approach each other by a screw movement, thereby reducing the distance between the driven gears 250. Accordingly, the plurality of second keys 261 mounted on the driven gear 250 move in a direction away from the driven shaft 241 along the plurality of second key grooves 257, thereby driving the driven gear 250.
  • the radius of rotation of the plurality of second keys 261 mounted on the is relatively smaller than when the shift does not occur.
  • the rotation radius of the plurality of first keys 231 mounted on the drive gear 220 is adjusted by the shift adjustment unit 281 of the plurality of second keys 261 mounted on the driven gear 250.
  • deceleration occurs by a ratio of the rotation radius of the plurality of first keys 231 and the rotation radius of the plurality of second keys 261.
  • the power input through the drive shaft 211 is driven by the drive gear 220, the plurality of first keys 231, the power transmission member 271, the plurality of second keys 261, and the driven gear ( 250 is sequentially passed through the driven shaft 241.
  • the deceleration occurs by a ratio of the rotation radius of the plurality of first keys 231 and the rotation radius of the plurality of second keys 261, the driven shaft 241 is rotated at a reduced speed with respect to the drive shaft 211.
  • the transmission structure is improved so that the speed change range can be adjusted by screwing motion without shifting by using hydraulic pressure, thereby making the transmission size compact compared to the prior art, thereby improving power transmission efficiency. It can be improved.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Theoretical Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Computer Networks & Wireless Communication (AREA)
  • Signal Processing (AREA)
  • Artificial Intelligence (AREA)
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Abstract

La présente invention concerne une transmission à variation continue. La transmission à variation continue selon la présente invention comprend un engrenage menant et un engrenage mené qui sont des engrenages coniques, et ainsi la transmission peut être formée en tant que structure compacte et l'efficacité de transfert de puissance peut également être améliorée.
PCT/KR2016/012040 2015-10-27 2016-10-26 Transmission à variation continue WO2017073993A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
KR10-2015-0149183 2015-10-27
KR20150149183 2015-10-27
KR1020150190643A KR101745807B1 (ko) 2015-12-31 2015-12-31 트레이 및 이를 구비하는 카드 커넥터
KR10-2015-0190643 2015-12-31

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WO2017073993A1 true WO2017073993A1 (fr) 2017-05-04

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PCT/KR2016/012040 WO2017073993A1 (fr) 2015-10-27 2016-10-26 Transmission à variation continue

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WO (1) WO2017073993A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110024535A (zh) * 2018-01-11 2019-07-19 北京林业大学 一种步进式苗盘的植苗驱动装置
CN110566642A (zh) * 2019-09-20 2019-12-13 付鹰波 机动车无级变速器
CN113309835A (zh) * 2021-05-13 2021-08-27 秦艳姣 一种瓣型双插入式无级变速器装置

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH04194440A (ja) * 1990-11-28 1992-07-14 Yasuo Ono チェーン式無段変速機
US20030050139A1 (en) * 2001-05-16 2003-03-13 Anderson Lawrence A. Variable drive transmission
JP2010060864A (ja) * 2008-09-04 2010-03-18 Konica Minolta Business Technologies Inc 画像形成装置
KR20110026855A (ko) * 2009-09-09 2011-03-16 최현환 이중 체인벨트 구동형 슬립리스 유단 변속장치

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH04194440A (ja) * 1990-11-28 1992-07-14 Yasuo Ono チェーン式無段変速機
US20030050139A1 (en) * 2001-05-16 2003-03-13 Anderson Lawrence A. Variable drive transmission
JP2010060864A (ja) * 2008-09-04 2010-03-18 Konica Minolta Business Technologies Inc 画像形成装置
KR20110026855A (ko) * 2009-09-09 2011-03-16 최현환 이중 체인벨트 구동형 슬립리스 유단 변속장치

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110024535A (zh) * 2018-01-11 2019-07-19 北京林业大学 一种步进式苗盘的植苗驱动装置
CN110566642A (zh) * 2019-09-20 2019-12-13 付鹰波 机动车无级变速器
CN110566642B (zh) * 2019-09-20 2023-02-03 付鹰波 机动车无级变速器
CN113309835A (zh) * 2021-05-13 2021-08-27 秦艳姣 一种瓣型双插入式无级变速器装置

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