JP2010510465A - Continuously variable transmission - Google Patents

Abstract

  What is disclosed in this specification is a continuously variable transmission. The continuously variable transmission includes a housing in which an input shaft is rotatably mounted to input power, an output unit that outputs power transmitted from the input shaft to the outside or receives a load from the outside, A torque converter provided between the input shaft and the output unit for converting the power torque transmitted from the input shaft or the output unit; and a rotational force disposed between the output unit and the torque converter. Is transmitted to the output unit, or is linked eccentrically to the torque conversion unit that receives a load from the output unit by its vertical reciprocating motion.

Description

  The present invention relates to a continuously variable transmission, and more particularly to a continuously variable transmission that can automatically increase or decrease an instantaneous torque output in accordance with an increase or decrease in load applied to an output shaft.

  However, the speed reducer outputs torque by decreasing the number of revolutions supplied from the power generator and increases the torque. When the load applied to the output shaft is larger than the output torque of the output shaft, The reverse load acts on the power generator such as the motor or the engine in reverse, thereby shortening the life of the motor or the engine.

  When a load larger than the output torque of the output shaft is applied to the motor or the engine, the intended output cannot be supplied to the output shaft.

  Therefore, the present invention has been made in view of the above problems, and even if the load on the output shaft is increased by automatically increasing or decreasing the torque of the output shaft according to the load applied to the output shaft, It is an aspect of the present invention to provide a continuously variable transmission that can prevent a load on an output shaft from being transmitted to a power source.

  Also provided is a continuously variable transmission capable of performing a driving operation at a constant speed even in the case of overload or no load by preventing increase / decrease in load applied to an output shaft from being transmitted to a power generator. Is another embodiment of the present invention.

  According to an aspect of the present invention, the above and other objects can be achieved by providing a continuously variable transmission, and the continuously variable transmission includes a housing on which an input shaft is rotatably mounted to input power. The power transmitted from the input shaft is output to the outside, or is provided between the input shaft and the output unit, and is transmitted from the input shaft or the output unit, and is provided between the output unit receiving the load from the outside. A torque conversion unit for converting the power torque, and the torque conversion unit disposed between the output unit and the torque conversion unit to transmit a rotational force to the output unit or to receive a load from the output unit by its vertical reciprocating motion. A link device eccentrically connected to the torque converter.

  The continuously variable transmission protects the power source by automatically increasing or decreasing the torque of the output shaft according to the load applied to the output shaft to prevent the output shaft load from being transmitted to the power source. be able to.

  The continuously variable transmission can prevent the increase or decrease of the load applied to the output shaft from being transmitted to the motive power generator, thereby performing a driving operation at a constant speed even in the case of overload or no load.

  The foregoing and other objects, features and advantages of the invention will be more clearly understood from the following detailed description taken in conjunction with the accompanying drawings in which:

  FIG. 1 is a perspective view illustrating a continuously variable transmission according to an embodiment of the invention.

  FIG. 2 is a perspective view illustrating the continuously variable transmission of FIG. 1 in which the output plate is separated from the housing;

  FIG. 3 is a perspective view illustrating the continuously variable transmission of FIG. 1 in which an input plate is separated from the housing.

  FIG. 4 is an exploded perspective view of the continuously variable transmission of FIG.

  5 is a perspective view of the continuously variable transmission of FIG. 1 in which the housing is separated;

  FIG. 6 is a perspective view of the continuously variable transmission of FIG. 1 viewed from below.

  FIG. 7 is an exploded view of the continuously variable transmission of FIG.

  FIG. 8 is a front view of the continuously variable transmission of FIG.

  FIG. 9 is a right side view of the continuously variable transmission of FIG.

  FIG. 10 is a left side view of the continuously variable transmission of FIG.

  FIG. 11 is a perspective view illustrating a lever crank of the continuously variable transmission of FIG.

  FIG. 12 is a perspective view illustrating a drive body of the continuously variable transmission of FIG.

  FIG. 13 is an exploded perspective view of the driving body of FIG.

  FIG. 14 is a cross-sectional view taken along the line II of the driver shown in FIG.

  FIG. 15 is an operation diagram of the lever crank of FIG.

  FIG. 16 is an operation diagram of forward and reverse rotation of the continuously variable transmission of FIG.

  FIG. 17 is a side view illustrating an elastic member that elastically supports the pressing device of the continuously variable transmission of FIG.

  FIG. 18 is a schematic view illustrating a continuously variable transmission according to another embodiment of the invention.

  FIG. 19 is a front view of the continuously variable transmission illustrated in FIG.

  20 is a front view of the continuously variable transmission of FIG. 18 in which the rotary inertia control device is separated,

  FIG. 21 is a plan view of the continuously variable transmission of FIG.

  22 is a left side view of the continuously variable transmission of FIG.

  FIG. 23 is a left side view illustrating a torque converter of the continuously variable transmission of FIG.

  24 is a longitudinal sectional view illustrating a power generator of the continuously variable transmission of FIG.

  Hereinafter, a continuously variable transmission according to a preferred embodiment of the present invention will be described in detail with reference to the accompanying drawings.

  As illustrated in FIGS. 1 to 17, the continuously variable transmission proposed in the present invention includes a housing 100 in which an input shaft 15 is rotatably mounted to input power, and power transmitted from the input shaft 15. Is output between the input shaft 15 and the output unit 112, and is transmitted from the input shaft 15 or the output unit 112. A torque converter 130 that converts the torque, and is arranged between the output part 112 and the torque converter 130, and is eccentrically connected to the torque converter 130 to transmit a rotational force to the output part 112 or its upper and lower And link devices 149 and 150 that receive a load from the output unit 112 by reciprocating motion.

  In the continuously variable transmission, the housing 100 is divided by a fixed plate 105 provided therein, and an output shaft 110 of the output unit 112 that transmits power to the outside is engaged with a central portion of the fixed plate 105, The lever shaft 132 and the rotation shaft 160 of the torque converter 130 are engaged with both sides of the fixed plate 105, respectively.

  An input plate 115 is provided on one side of the housing 100 to insert the input shaft 15 of the power unit 10 rotatably, and an output plate 120 is provided on the other side to insert the output shaft 110 rotatably.

  The input shaft 15 is connected to a power source such as a motor or an engine to transmit rotational power. The input shaft 15 is provided in the drive gear 20 and transmits rotational power to the torque converter 130.

  The torque converter 130 includes a lever shaft 132 that is rotatably mounted on the fixed plate 105 of the housing 100, and a gear member that is provided on one side of the lever shaft 132 to which rotational power is transmitted from the torque converter 130. 170 and a circular member 165 provided on the other side of the lever shaft 132.

  In the torque converter 130, the gear member 170 includes a driven gear 171 on the outer peripheral surface thereof, and the driven gear 171 is meshed with the drive gear 20. Therefore, the rotational power can be transmitted from the input shaft 15 to the torque converter 130.

  The first rack gear 141 is movably mounted inside the gear member 170, and the first rack gear 141 is elastically supported by a first spring 138. Therefore, the first rack gear 141 is moved outside the center of the lever shaft 132 while being supported by the first spring 138.

  More specifically, the linear groove 145 is formed inside the gear member 170, and the pair of guide members 172 are engaged inside the linear groove 145. Accordingly, the first rack gear 141 is slidably engaged with the guide member 172.

  One side of the first spring 138 is inserted into a support recess 146 formed inside the first rack gear 141, and the other side is supported by the inner bottom surface of the gear member.

  Accordingly, the first spring 138 elastically supports the first rack gear 141 radially outward.

  The circular member 165 has the same structure as the gear member 170, and the circular member 165 and the gear member 170 are arranged symmetrically with respect to the pinion gear 135.

  That is, the second rack gear 140 is movably engaged inside the circular member 165, and the second rack gear 140 is elastically supported by the second spring 137. Accordingly, the second rack gear 140 is moved outside the center of the lever shaft 132 while being supported by the second spring 137.

  A straight groove 145 is formed inside the circular member 1645, and a pair of guide members 172a are engaged with the inside of the straight groove 145. Accordingly, the second rack gear 140 is slidably engaged with the guide member 172a.

  One side of the second spring 137 is inserted into a support recess formed in the second rack gear 140, and the other side is supported by the inner bottom surface of the circular member 165.

  Accordingly, the second spring elastically supports the second rack gear 140 outward in the radial direction.

  The first and second rack gears 141 and 140 are connected to each other by the pinion gear 135. That is, when the first rack gear 141 is pulled up, the second rack gear 140 is lowered by the rotation of the pinion gear 135, and when the first rack gear 141 is lowered, the second rack gear 140 is rotated by the rotation of the pinion gear 135. Pulled up by.

  Accordingly, the first and second rack gears 141 and 140 can be moved by the pinion gear 135 by the same distance.

  First and second rotary pins 174 and 175 capable of engaging the first and second rotary plates 151 and 152 of the link devices 149 and 150 with the side surfaces of the first and second rack gears 141 and 140, respectively. Provided in the first and second rack gears 141 and 140, respectively.

  First and second engaging recesses 148 are formed on the inner surfaces of the first and second rack gears 141 and 140, respectively, and the first and second rotating pins 174 and 175 are inserted into the engaging recesses 148, respectively. The

  Next, since the first and second engaging recesses 148 are formed to be displaced from the center of the lever shaft 132, the first and second engaging recesses 148 are inserted into the first engaging recesses 148. Also, the second rotation pins 174 and 175 are also displaced from each other.

  As a result, when the first and second arms 154 and 155 of the link devices 149 and 150 connected to the first and second rotating pins 174 and 175 are moved in the vertical direction, they have opposite phases.

  In order to adjust the eccentric distance between the first and second rotating pins 174 and 175 and the rotation center thereof, an adjusting screw 176 is provided on the rotating pins 174 and 175 of the first and second rack gears 140 and 141.

  The adjustment screw 176 includes a head 177 and an adjustment hole 178 is formed in the circular member 165 and the gear member 170. The head 177 of the adjustment screw 176 can be rotated by inserting a tool such as a hexagon wrench into the adjustment hole 178.

  Accordingly, when the adjusting screw 176 is rotated, the first and second rotating pins 174 and 175 are also moved, and the first and second rotating pins engaged with the first and second rotating pins 174 and 175, respectively. The eccentric distances of the rack gears 140 and 141 can also be adjusted because they are moved along the guide members 172 and 172a.

  The first and second arms 154 and 155 of the link devices 149 and 150 are connected to the first and second rotating pins 174 and 175, respectively, and the torque converter 130 is driven to output power to the power output. When transmitted to the unit 112, it is alternately moved up and down.

  The link devices 149 and 150 include a first lever crank 149 and a second lever crank 150. The first lever crank 149 and the second lever crank 150 have the same structure and are symmetrical to each other. Be placed.

  More specifically, the first lever crank 149 includes a first rotating plate 151 connected to the first rotating pin 175 and a first arm 154, one side of which is a hinge to the first rotating plate 151. The other end is coupled to the rotating shaft 160 of the power output unit 112 to transmit power.

  One side of the first rotating plate 151 is hinged to the first rotating pin 174, and the other side is hinged to the first arm 154.

  Accordingly, when the first rotation pin 174 is rotated along a circular locus, the first arm 154 is formed vertically as the first rotation plate 151 is moved in cooperation with the first rotation pin 174. It is moved along the trajectory.

  One side of the first arm 154 is connected to the first rotating pin 174 by the first rotating plate 151, and the other side is connected to the rotating shaft 160 by an engaging plate 157.

  The first arm 154 of the engagement plate 157 includes a one-clutch therein, and the one-clutch 158 is connected to an outer peripheral surface of the rotating shaft 160 that is rotatably engaged with the housing 100.

  Also, the second lever crank 150 has the same structure as the first lever crank 149. That is, the second lever crank 150 includes the second rotating plate 152 and the second arm 155.

  The engagement plate 157a is provided on the other side of the second arm 155, and a one-way clutch 158a is provided. Accordingly, the second arm 155 is connected to the outer peripheral surface of the rotating shaft 160 by the one-way clutch 158a.

  As described above, the first and second lever cranks 149 and 150 are coupled to the rotary shaft 160 by the one-way clutches 158 and 158a in a state of being arranged symmetrically with each other.

  As the first and second arms 154 and 155 are alternately moved in the vertical direction, the rotary shaft 160 can be rotated.

  That is, when the first arm 154 is lowered by the power transmitted from the torque converter 130, the one-way clutch 158 is rotated in the counterclockwise direction, and the rotating shaft 160 is also rotated in the counterclockwise direction. .

  Next, since the second arm 155 is rotated in the clockwise direction, that is, in the direction opposite to the first arm 154, the second one-way clutch 158a connected to the second arm 155 transmits power to the second arm 155. Without being transmitted to the rotating shaft, the rotating shaft 160 is rotated in the clockwise direction.

  On the other hand, when the first arm 154 is pulled up, the one-way clutch 158 is rotated in the clockwise direction without transmitting power to the rotating shaft.

  Next, since the second arm 155 is rotated in the counterclockwise direction, that is, in the direction opposite to the first arm 154, the second one-way clutch 158a connected to the second arm 155 has the rotation shaft. Rotate 160 clockwise.

  As a result, the first and second arms 154 and 155 can rotate the rotating shaft 160 alternately.

  When the load on the output shaft 110 increases during the rotation of the rotary shaft 160, the rotary shaft 160 transmits the load to the torque converter 130 in the reverse direction by the first and second arms 154 and 155. To do.

  Next, the torque converter 130 increases an instantaneous torque for operating the first and second lever cranks 149 and 150.

  Furthermore, since the increased torque is transmitted to the first and second rack gears 141 and 140, the first and second rack gears 141 and 140 press the first and second springs 137 and 138, respectively.

  Accordingly, the first and second rack gears 141 and 140 are moved along the guide member 172 toward the rotation center of the lever shaft 132 to absorb the increased load.

  When the load on the output shaft 110 further increases, the first and second rotation pins 174 and 175 of the first and second rack gears 140 and 141 are moved to the center rotation of the lever shaft 132, and the eccentric distance is increased. Set to zero.

  Accordingly, since the first and second rotating plates 151 and 152 are positioned on the same line as the central rotation of the lever shaft 132, the first and second rotating plates can be used even when the lever shaft 132 is rotated. 151 and 152 are not rotated and do not affect the load on the power unit 10.

  On the other hand, when the load on the rotating shaft 160 returns to the normal state or decreases, the instantaneous torque that can operate the first and second lever cranks 149 and 150 also decreases. The two rack gears 140 and 141 are returned to their original positions by the elastic force of the springs 137 and 138.

  Accordingly, the torque converter 130 can perform a driving operation in a normal state.

  Since the first and second arms 154 and 155 are preferably made of carbon steel, the strength is sufficient to transmit power from the end portions of the first and second arms 154 and 155 to the other end. Can be maintained. Further, a plurality of through holes 156 are formed in the first and second arms 154 and 155 to reduce the weight thereof.

  Since the first and second arms 154 and 155 of the first and second lever cranks 149 and 150 are arranged symmetrically with each other, vibration caused by the movement of the first and second arms 154 and 155 can be canceled.

  That is, when the lever cranks 149 and 150 are moved, the first and second arms 154 and 155 fluctuate on both sides of the housing, and thus the first and second arms 154 with respect to the housing 100. , 155 to balance the moments of inertia so that vibrations caused by the deviation of the moments of inertia can be prevented from being symmetric.

  The output unit 112 is rotatably provided in the housing 100 and is rotated in cooperation with the link devices 149 and 150, and ends of the first and second arms 154 and 155. The first and second one-side clutches 158 and 158a that transmit the rotational force in one direction to the rotating shaft 160, and the output shaft 110 that outputs the rotational power transmitted from the rotating shaft 160 to the outside. And direction changing members 180 and 185 that are provided between the rotary shaft 160 and the output shaft 110 and convert the rotation direction of the output shaft into a forward direction or a reverse direction.

  Each of the direction changing members 180 and 185 meshes with the rotating gear 161 of the rotating shaft 160 and selectively transmits the rotational power to the output shaft 110, and the output shaft 110 moves. And a conversion gear 185 that is engaged and selectively meshed with the rotation shaft 160 or the intermediate gear 180 to change the rotation direction of the output shaft 110.

  The intermediate gear 180 is connected to the front gear 182 that is always meshed with the rotating gear 161 of the rotating shaft 160 and the rear gear 183 that is coupled to the rear side of the front gear 182 and meshed with the conversion gear 185 of the output shaft 110. And are included.

  Accordingly, when the conversion gear 185 moves in the positive direction along the output shaft 110 so as to mesh with the rotation gear 161, the rotational power of the rotation gear 161 rotated counterclockwise is converted to the conversion gear 185. Therefore, the conversion gear 185 is rotated in the clockwise direction to rotate the output shaft 110 in the forward direction, and then the front gear 182 is meshed with the rotation gear 161 and is in an idling state. .

  On the other hand, when the conversion gear 185 is moved backward along the output shaft 110 such that the conversion gear 185 is connected to the rear gear of the intermediate gear 180, the rotational power of the rotary gear 161 rotated counterclockwise is Since it is transmitted to the front gear 182, the front gear 182 is rotated in the clockwise direction. Further, when the front gear 182 is rotated in the clockwise direction, the rear gear 183 is also rotated in the clockwise direction, so that the conversion gear 185 can be rotated in the counterclockwise direction (reverse direction). it can.

  As described above, as the conversion gear 185 is moved in the front-rear direction along the output shaft 110, the output shaft 110 is rotated in the forward direction or the reverse direction.

  Further, the pressing device 192 is provided outside the housing 110 and moves the conversion gear 185 in the front-rear direction.

  The pressing device 192 is connected to the horizontal shaft 193 rotatably attached to the housing 100, a vertical plate 194 vertically attached to one side of the horizontal shaft 193, and the other side of the horizontal shaft 193. A knob 195 and a circular body 190 connected to the vertical plate 194 to move the conversion gear 185 in the front-rear direction are included.

  The knob 195 is disposed outside the housing 100 so as to be easily rotated, and the horizontal shaft 193 is rotated by rotating the knob 195, and the vertical plate 194 connected to the horizontal shaft 193. Is also rotated. When the vertical plate 194 is rotated, the circular body is moved in the front-rear direction.

  Next, the circular body 190 is inserted into a recess 187 formed in the conversion gear 185.

  Therefore, when the knob 195 is pushed or pulled, the circular body 190 presses the inner wall of the recess 187 and moves the conversion gear 185 in the front-rear direction.

  As illustrated in FIG. 17, an elastic member 196 is provided on the pressing device 192 so that the knob 195 can be easily moved in the front-rear direction.

  The elastic member 196 includes a first elastic body 197 provided on the front side of the circular body 190 engaged with the input shaft 15 and a second elastic body 198 provided on the rear side of the circular body 190. included.

  The first elastic body 197 elastically supports the conversion gear 185 in the forward direction, and the second elastic body 198 elastically supports the elastic member 196 in the backward direction.

  Therefore, when the knob 195 is pushed in the forward direction for changing the direction, the conversion gear 185 can be easily moved in the forward direction by the elastic force of the first elastic body 197.

  On the other hand, when the knob 195 is pushed backward, the conversion gear 185 can be easily moved backward by the elastic force of the second elastic body 198.

  As described above, since the pressing device 192 is elastically supported by the elastic member 196, the forward rotation and the reverse rotation of the output shaft 110 can be easily achieved.

  18 to 24 illustrate a continuously variable transmission according to another embodiment of the present invention. The continuously variable transmission according to this embodiment has the same structure as the above-described device, and detailed description of the same elements will not be repeated.

  As illustrated in FIGS. 18 to 24, the continuously variable transmission proposed in this embodiment of the present invention has a housing 242 on which an input shaft 202 is rotatably mounted to input power, and transmission from the input shaft 202. The output unit 240 that outputs the generated power to the outside or receives a load from the outside, and is provided between the input shaft 202 and the output unit 240, and is transmitted from the input shaft 202 or the output unit 240. A torque conversion unit 210 that converts the power torque, and is disposed between the output unit 240 and the torque conversion unit 210 and is eccentrically connected to the torque conversion unit 210 to transmit a rotational force to the output unit 240, Or the link apparatus 270 which receives a load from the said output part 240 by the up-and-down reciprocating motion is included.

  In the continuously variable transmission, the torque converter 210 is connected to the input shaft 202 that transmits the power of the power unit 300 such as a motor or an engine to the outside.

  As the eccentric radius of the input shaft 202 is changed by a load applied from the outside, a rotating pin 217 for adjusting the torque transmitted to the outside is connected to the input shaft 202. The rotating pin 217 is elastically supported by a spring 215 on the front side of the input shaft 202, and when an external load is applied, the eccentric distance thereof is adjusted in the radial direction of the input shaft 202.

  Here, the elastic device may be an elastic member that supports the rotating pin 217 and the spring 215. For example, an air cylinder that is elastically compressible and can return the rotating pin 217 to its original position may be employed as the elastic device.

  The torque converter 210 is connected to the input shaft 202 of the power unit 300 so as to rotate, the linear pin passage along which the rotating pin 217 slides and the spring 215 is disposed is the torque converter. It is formed on the front side of 210.

  The inclined annular flange 222 is provided outside the linear passage 218, and the annular flange 222 is connected to the cylindrical torque conversion housing 220.

  A roller 125 supported by the inner peripheral wall of the annular flange 222 is provided on one side of the torque converter 210, and a pressing pin 230 supported by the rotating pin 217 is provided on the other side.

  Next, the distance between the center line of the rotating pin 217 and the torque conversion housing 220 is adjusted by moving the torque conversion housing 220 linearly and pressing the pressing pin 230 with the annular flange 222. Can do.

  In the torque converter 210, when the torque converter housing 220 is moved to the front side of the input shaft 202, the roller moves to the rear side of the annular flange 222 along the inclined inner peripheral wall of the annular flange 222. Is done.

  Next, as the pressing pin 230 is pressed and the pressing pin 230 compresses the rotating pin 217, the spring 215 is compressed to reduce the eccentric distance of the rotating pin 217, so that the rotating pin 217 receives the input. Close to the axis 202 centerline.

  Accordingly, the eccentric radius of the rotary pin 217 can be fixed to the input shaft 202 after the torque conversion housing 220 is fixed.

  Next, when the external load continuously increases, the rotation pin 217 needs to be moved to the position of the linear passage 218 of the torque conversion housing 220 to the maximum, and the center of the input shaft 202 of the rotation pin 217 When the eccentric distance from the line becomes zero, the rotation pin 217 is rotated only between the input shaft 202 and the link device 270.

  Accordingly, since the arm 272 of the link device 270 cannot be moved in the vertical direction, there is no output transmitted to the power output unit 240 via the link device 270 and to the power unit via the input shaft 202. The transmitted external load becomes zero, thereby preventing the continuously increasing external load from affecting the power unit 200 and protecting the power unit 200 from overload.

  Further, the torque conversion housing 220 includes a rotary inertia control device, which uniformly adjusts the deviation of the mass distribution with respect to the center line of the input shaft 202.

  That is, since the balance weight 236 is disposed in the linear passage of the torque conversion housing 220, the eccentric distance can be adjusted on the opposite side of the center line of the input shaft 202 in accordance with the sliding of the rotary pin. it can.

  The balance weight 236 makes the mass distribution of the rotation pin 217 uniform, and prevents the torque conversion housing 220 from being vibrated due to the rotation pin 217 during high-speed rotation of the input shaft 202. The occurrence of vibration of the input shaft 202 is prevented, thereby preventing the bearing of the input shaft 202 from being damaged.

  Then, the balance weight 236 can be connected to a wire 238 wound around a winding roller 237 rotated by a horizontal movement of the torque conversion housing 220 or the soft linear member.

  That is, the balance weight 236 is disposed below the winding roller 237 and connected to one side of the wire 238 wound around the winding roller 237, and the other end 238a of the wire 238 is connected to the winding roller 237. The roller 237 is connected to the lower end of the pressing pin 230 disposed on the lower side of the roller 237.

  Accordingly, the pressing pin is pressed by the inner surface of the annular flange 222 of the torque conversion housing 220 so as to be moved downward, and the rotation pin 217 is moved to the center line of the torque conversion housing 220 by the movement of the pressing pin 230. When approaching and reducing its eccentric distance from the input shaft 202, the other end 238a of the wire 238 is moved downward as the pressing pin 230 is lowered and the balance weight connected to one side of the wire 238. 236 is moved upward, thereby reducing the eccentric distance of the balance weight 236 from the centerline of the torque converter housing 220.

  As the torque conversion housing 220 is moved to the rear side of the input shaft 202, the roller 125 is moved to the front side of the annular flange 222 along the inclined inner peripheral wall of the annular flange 222. Further, the pressing pin 230 is loosened in the radial direction of the input shaft 202 by the pressing operation of the rotating pin 217 to which the elastic force of the spring 215 is applied, and thereby the eccentric distance of the rotating pin 217 from the input shaft 202. Increase.

  That is, when the pressing pin 230 is loosened from the inner surface of the annular flange 222 of the torque conversion housing 220 so as to move upward, the rotation pin 217 is spaced from the center line of the torque conversion housing 220. . Next, since the other end 238a of the wire 238 is moved upward, the length of the wire 238 from the winding roller 237 on which the balance weight is suspended is increased, and the balance weight 236 is Corresponding to the pin 217, the torque conversion housing 220 moves away from the center line.

  As described above, the wire 238 to which the balance weight 236 is connected is wound around the winding roller 237 by adjusting the eccentric distance of the rotating pin 217 adjusted by the pressing pin 230 from the input shaft. Alternatively, since the winding is released, the eccentric distance of the balance weight 236 from the input shaft 202 can be automatically adjusted.

  The link device 270 includes an arm 272 whose one end is fixed to the driven shaft 245 of the power output unit and rotates the driven shaft 245 in the forward or reverse direction during vertical reciprocation.

  One end of the link device 270 is connected to the rotation pin 217 that revolves around the rotation center of the torque conversion housing 220, and the other end is connected to the arm 272.

  Next, as the rotation pin 217 is rotated by the rotation of the torque conversion housing 220, the rotation plate 275 engaged with the rotation pin 217 moves around the rotation center of the torque conversion housing 220 together with the rotation pin 217. It revolves around the rotating pin 217.

  Accordingly, the connecting portion 272 a of the arm 272 connected to the rotating pin 217 is reciprocated up and down of the torque conversion housing 220. The fixed portion 272b of the arm fixed to the driven shaft 245 is fixed to the driven shaft 245 so as to be rotated in the forward direction or the reverse direction. The driven shaft 245 is fixed to the fixed portion 272b of the arm 272. It is rotated in the forward and reverse direction as it is rotated in the direction or the reverse direction.

  Next, the mechanism by which the rotational power of the power unit 300 is transmitted to the driven shaft 245 by the link device 270 is the same as the lever crank mechanism related to the four-bar link.

  That is, the lever crank mechanism has a first link as a fixed base, a second link whose one end is engaged with the first link, and one end engaged with the other end of the second link. The third link is a third link that exists in the space, and a fourth link having one end engaged with the other end of the second link, and the other end being the second link. And a fourth link characterized in that the first link is engaged with the first link.

  In the lever crank mechanism, the second link provided on one side of the base is rotated in the base, and the fourth link connected to the second link is changed by the third link.

  Accordingly, the first link is a fixed portion of the torque conversion housing 220 and a fixed portion of the driven shaft 245, and the second link corresponds to the torque conversion housing 220 and the rotation pin 217, and Three links correspond to the rotating plate 275, and the fourth link corresponds to the arm 272.

  Since the link device 270 has a mechanism similar to the lever crank mechanism having a four-joint link, the rotating plate 275 can be removed or replaced with a link mechanism engaged with a sliding passage that can be formed in the arm 272. It is also possible to do.

  Next, the sliding passage is linearly formed at the end of the arm 272, and the end of the rotating pin 217 is connected to the sliding passage.

  The output unit 240 includes a case 242 that is fixed to the power unit 200. In the case, the driven shaft 245 and the output shaft 250 are disposed in parallel with the input shaft 202, and the upper shaft 260 is disposed between the driven shaft 245 and the output shaft 250.

  Since the driven shaft 245 includes a one-way clutch 249, the driven shaft 245 rotates idle in one direction and rotates in the other direction together with the driven shaft 245. The first and second clutch teeth 247 and 248 are attached to the outer periphery of the driven shaft 245.

  The first clutch teeth 247 are positioned on the left side of the driven shaft 245 and are rotated together with the driven shaft 245 by the clockwise rotation of the driven shaft 245 transmitted from the torque converter 210 to the driven shaft 245. Further, the driven shaft 245 can idle in the counterclockwise direction by the one-way clutch 249.

  The second clutch teeth 248 are positioned on the right side of the driven shaft 245, and in contrast to the first clutch teeth 247, the driven shaft 245 is transmitted to the driven shaft 245 by the counterclockwise rotation of the driven shaft 245. It is rotated with the shaft 245. Further, the driven shaft 245 can idle in the clockwise direction by the one-way clutch 249.

  Next, the clutch bearing 249 is rotated in one direction with respect to the shaft, and is rotated in the other direction together with the shaft.

  In the case 242, the rotating tooth 252 coupled to the output shaft 250 so as to be idled and meshed with the first clutch tooth 247, and the output so as to be meshed with or separated from the second clutch tooth 248. A movable tooth 255 slid from the shaft 250, a fixed tooth 262 fixed to the upper shaft 260, the left side meshing with the rotating tooth 252, and the right side meshing with the second clutch tooth 248. Provided.

  Next, the movable tooth 255 is provided on the output shaft 250 so as to be rotated with the output shaft 250 or to be slid from the output shaft 250.

  The moving device 263 of the movable tooth 255 fixes one side of the movable tooth 255, and this fixing is made possible by a ring member 265 that can rotate the movable tooth 255. Then, the ring member 265 may include a handle 167 for moving the ring member 265.

  Here, simple structures such as the ring member 265 and the handle 267 can be applied to the structure in which the movable tooth 255 is moved along the output shaft 250 even in various structures. For example, the structure can be automatically realized by an actuator such as a linear motor, a cylinder, and a stepping motor.

  Next, the movable tooth 255 is moved to the left side of the output shaft 250 so as to mesh with the fixed tooth 262, moved to the right side so as to mesh with the second clutch tooth 248, and the second clutch tooth. 248 is meshed with the left side of the fixed tooth 262 to be rotated.

  Hereinafter, the operation of the continuously variable transmission according to the second embodiment of the present invention will be described in detail.

  First, when the shaft is rotated by supplying a power source to the power unit 300, the rotational power of the power unit 300 rotates the torque conversion unit 210, and the rotation pin 217 of the torque conversion unit 210 The rotation plate 275 is rotated eccentrically from the center line of the torque converter 210, and the rotating plate 275 is rotated by the rotation of the rotating pin 217.

  Accordingly, the arm 272 is reciprocated in the vertical direction to rotate the driven shaft 245 in the forward direction or the reverse direction.

  Next, when the driven shaft 245 is rotated clockwise, that is, in the positive direction by the arm 272, the first clutch teeth 247 are rotated together with the driven shaft 245 by the clockwise rotation of the driven shaft 245. The

  The rotation of the first clutch teeth 247 causes the rotation teeth 252 engaged with the output shaft 250 to idle in the counterclockwise direction, that is, the reverse direction, by the bearings. The fixed tooth 262 of the shaft 260 is rotated in the positive direction.

  Here, since the fixed tooth 262 is engaged with the second clutch tooth 248 of the driven shaft 245, the second clutch tooth 248 is rotated in the reverse direction.

  Next, the reverse rotation of the second clutch teeth 248 results in an idling operation in which the driven shaft 245 is not rotated, and the second clutch teeth 248 transmits the rotational power to the output shaft 250 and the output shaft 250 It meshes with the movable tooth 255 positioned at the left end.

  Accordingly, the movable tooth 255 is rotated in the positive direction, and the positive rotation of the movable tooth 255 rotates the output shaft 250 in the positive direction.

  On the other hand, when the driven shaft 245 is rotated counterclockwise by the arm 272, that is, in the reverse direction, the first clutch teeth 247 of the driven shaft 245 are idled and the second clutch teeth 248 are rotated by the driven shaft 245. And rotated in the opposite direction.

  Next, since the second clutch teeth 248 are engaged with the movable teeth 255 of the output shaft 250, the movable teeth 255 are rotated in the positive direction, and the output shaft 250 is rotated in the positive direction.

  The reverse rotation power of the second clutch teeth 248 is transmitted to the fixed teeth 262, causing the fixed teeth 262 to rotate in the forward direction. Further, the fixed tooth 262 rotates the rotating tooth 252 in the reverse direction, and the rotating tooth 252 rotates the first clutch tooth 247 in the forward direction.

  Accordingly, the forward rotation of the first clutch teeth 247 is idled by the clutch bearing 249 of the driven shaft 245.

  The above description relates to a case where the movable tooth 255 is positioned at the right end portion of the output shaft 250, and the output shaft 250 is moved in the forward direction by forward / reverse rotation of the driven shaft 245 due to vertical reciprocation of the arm 272. It relates to the output that is rotated in the direction.

  On the other hand, when the movable tooth 255 is moved from the right end portion of the output shaft 250 to the right side, the movable tooth 255 is separated from the second clutch tooth 248 and meshed with the left side portion of the fixed tooth 262. Accordingly, the output shaft 250 can be rotated in the reverse direction by the forward rotation of the driven shaft 245 for the arm 272.

  That is, the driven shaft 245 is rotated in the forward direction, the first clutch teeth 247 are rotated in the forward direction, and then the rotating teeth 252 are rotated in the reverse direction by the first clutch teeth 247.

  The fixed teeth 262 are rotated in the forward direction by the rotating teeth 252, the movable teeth 255 are rotated in the reverse direction by the fixed teeth 262, and the output shaft 250 is rotated in the reverse direction by the movable teeth 255.

  The second clutch 248 is meshed with the fixed teeth 262, and thus is rotated in the reverse direction by the forward rotation of the fixed teeth 262. Next, the reverse rotation of the second clutch teeth 248 does not affect the forward rotation of the driven shaft 245 because the idle rotation is performed with respect to the driven shaft 245.

  Further, when the driven shaft 245 is rotated in the reverse direction by the arm 272, the first clutch tooth 247 rotates idly and the second clutch tooth 248 is rotated in the reverse direction together with the driven shaft 245.

  Accordingly, the fixed tooth 262 is rotated in the forward direction by the second clutch tooth 248, the movable tooth 255 is rotated in the reverse direction by the second clutch tooth 248, and the output shaft 250 is further rotated by the movable tooth 255. It is rotated in the opposite direction.

  Next, the forward rotation of the fixed tooth 262 rotates the rotating tooth 252 in the reverse direction, and the first clutch tooth 247 is rotated in the forward direction by the rotating tooth 252.

  Accordingly, the forward rotation of the first clutch teeth 247 results in the idling operation of the driven shaft 245 and thus does not affect the reverse rotation of the driven shaft 245.

  As described above, the forward rotation and the reverse rotation of the output shaft 250 can be selectively converted according to the position of the movable tooth 255, and the power of the power unit 300 is transmitted to the outside through the output shaft 250.

  When the output shaft 250 transmits power to the industrial machine, the load converted in the initial stage of the operation of the industrial machine or the load due to the conversion of the load applied to the industrial machine itself is applied to the output shaft 250. .

  Next, as the load on the output shaft 250 increases, the load on the driven shaft 245 that transmits the rotational power to the output shaft 250 increases, and the arm 272 rotates the driven shaft in the direction opposite to the forward direction. The transmitted load also increases.

  Further, as the load on the arm 272 increases, the load transmitted to the rotating plate 275 connected to the arm 272 also increases.

  As the load on the rotating plate 275 increases, the load on the rotating pin 217 engaged with the rotating plate 275 increases, and as the load on the rotating pin 217 increases, the rotating pin 217 is supported by the spring. Thus, the load on the eccentrically arranged torque conversion housing 220 is increased.

  As the load on the torque conversion housing 220 increases, the load on the input shaft 202 that rotates the torque conversion housing 220 also increases, so the load on the power unit 300 that rotates the input shaft 202 increases.

  Next, the increased load on the rotating plate 275 is not transmitted to the power unit as it is, but is applied as a force for pressing the rotating pin 217 that can move in the radial direction from the center line of the torque conversion housing 220.

  Accordingly, the rotating pin 217 moves the spring to the center line of the torque conversion housing 220 and compresses the spring 215.

  That is, the rotating pin 217 is moved toward the center line of the input shaft 202 of the power unit 300 while compressing the spring 215, and the eccentric distance of the rotating pin 217 from the center line of the input shaft 202 is reduced. Is done.

  Accordingly, the instantaneous torque of the rotating pin 217 transmitted to the input shaft 202 of the power unit 300 is reduced, the load of the power unit 300 is not increased, and the normal state is maintained.

  Therefore, after the load on the output shaft 250 is increased, the instantaneous torque applied to the rotary pin 217 by the input shaft 202 of the power unit 300 is reduced, and the load on the power unit 300 is not increased. The rotational speed of 217 is not reduced and remains normal.

  Further, since the rotation radius of the rotary pin 217 is reduced, the vertical displacement of the arm 272 is reduced.

  As described above, the principle of preventing overload of the motor by increasing the load of the output shaft 250 and changing the rotation radius of the rotation pin 217 is a principle related to the universal law of rotational energy, The rotation radius of 217 is decreased by increasing the load of the output shaft 250, and the forward / reverse rotation angle of the driven shaft 245 and the output rotation speed of the output shaft 250 are decreased by decreasing the displacement of the arm 272. Thus, the instantaneous torque of the output shaft 250 is increased.

  Here, the rotational energy corresponding to the power of the power unit 200 and the output generated by the power unit 300 is adjusted so that the position change of the rotation pin 217 is adjusted by the torque conversion unit 210. Not converted by load and displacement conversion.

  Accordingly, when the load on the output shaft 250 increases, the rotational speed of the output shaft 250 decreases, the output torque of the output shaft 250 increases, and when the load on the output shaft 250 decreases, the output shaft 250 increases. And the output torque of the output shaft 250 is decreased.

  That is, even when the load of the output shaft 250 is converted to an overload, the overload that increases the output torque of the power unit 300 is not transmitted to the power unit 300, so that the safe operation of the power unit 300 is performed. Can be secured.

  The present invention relates to a continuously variable transmission, and more particularly to a continuously variable transmission that can automatically increase or decrease an instantaneous torque output in accordance with an increase or decrease in a load applied to an output shaft.

  The present invention relates to a continuously variable transmission, and more particularly to a continuously variable transmission that can automatically increase or decrease an instantaneous torque output in accordance with an increase or decrease in a load applied to an output shaft. The preferred embodiments of the present invention have been disclosed for illustrative purposes, and those skilled in the art will recognize that various embodiments can be made without departing from the scope and true spirit of the invention as disclosed in the appended claims. It will be understood that changes, additions and substitutions may be made.

Claims (17)

  In a continuously variable transmission, a housing in which an input shaft is rotatably mounted to input power, an output unit that outputs power transmitted from the input shaft to the outside or receives a load from the outside, and the input shaft And a torque converter that is provided between the output part and converts the power torque transmitted from the input shaft or the output part, and is arranged between the output part and the torque converter, and the rotational force is A continuously variable transmission comprising: a link device that is transmitted to the output unit or eccentrically connected to the torque conversion unit that receives a load from the output unit by its vertical reciprocating motion.   The continuously variable transmission according to claim 1, wherein the torque converter is rotatably attached to the housing and engaged with one side of the lever shaft, and a lever shaft that transmits the rotational power to the link device. And a gear member that meshes with the input shaft and transmits the rotational power thereof, and a circular member that is engaged with the other side of the lever shaft to which the rotational power of the gear member is transmitted. Continuously variable transmission.   3. The continuously variable transmission according to claim 2, wherein the circular member or the gear member is slidable inside the first and second guide members provided therein and the first and second guide members, respectively. The first and second rack gears engaged with each other, and the first and second rack gears are pressed radially outward by elastically supporting the first and second rack gears, respectively. Two-stage, a pinion gear provided between the first and second rack gears, and first and second rotating pins respectively provided on the outer surfaces of the first and second rack gears. Transmission device.   4. The continuously variable transmission according to claim 3, wherein an eccentric distance of the rack gear from the rotation center of the lever shaft is adjusted by screwing an adjustment screw to the rack gear.   The continuously variable transmission according to claim 2, wherein the link device includes a first rotating plate coupled to a first rotating pin of the first rack, one side of which is hinged to the first rotating plate, and the other side of the first rotating plate. A first arm connected to the output unit for transmitting power; a second rotating plate connected to a second rotating pin of the second rack; and one side hinged to the second rotating plate and the other side A continuously variable transmission comprising: a second arm connected to the output unit to transmit power.   6. The continuously variable transmission according to claim 5, wherein the first arm and the second arm are arranged symmetrically to each other.   6. The continuously variable transmission according to claim 5, wherein the output portion is provided at each of an output side rotatably provided in the housing, and ends of the first arm and the second arm, respectively. First and second one-way clutches that transmit rotational power to the output shaft, and a direction changing member that is provided between the rotary shaft and the output shaft and converts the rotational direction of the output shaft in the forward direction or the reverse direction. And a continuously variable transmission.   The continuously variable transmission according to claim 7, wherein the direction changing member is provided between the rotating shaft and the output shaft, and selectively transmits the rotational power to the output shaft and the output shaft. A conversion gear that is movably engaged with the rotation shaft and selectively meshed with the rotation gear of the rotation shaft or the intermediate gear to change the rotation direction of the output shaft. Step transmission.   9. The continuously variable transmission according to claim 8, wherein the intermediate gear is connected to the rear side of the front gear, which is always engaged with the rotary gear of the rotary shaft, and meshed with the conversion gear of the output shaft. A continuously variable transmission.   9. The continuously variable transmission according to claim 8, wherein the housing further includes a pressing device, and the pressing device is mounted vertically on one side of the horizontal shaft and a horizontal shaft that is rotatably mounted on the housing. A continuously variable transmission comprising: a vertical plate; a knob connected to the other side of the horizontal shaft; and a circular body connected to the vertical plate to move the conversion gear in the front-rear direction. .   9. The continuously variable transmission according to claim 8, wherein the pressing device further includes an elastic member, and the elastic member is provided on a front side of the circular body engaged with the drive shaft to thereby adjust the conversion gear. A continuously variable transmission comprising: a first elastic body that presses in a direction; and a second elastic body that is provided on the rear side of the circular body and presses the conversion gear in a backward direction.   The continuously variable transmission according to claim 1, wherein the torque converter absorbs a load as the rotating pin is moved in a rollover state, and a rotating pin connected to the input shaft so as to be eccentrically rotated. A stepless torque converting housing, and a stepless pin having one end engaged with a roller supported by an inner peripheral wall of the torque converting housing and the other end supported by the rotating pin. Transmission device.   The continuously variable transmission according to claim 12, wherein the torque conversion housing in which a spring is disposed includes a linear passage provided on a front side thereof, and an inclined annular flange provided on a peripheral portion on the front side thereof. A continuously variable transmission comprising the continuously variable transmission.   The continuously variable transmission according to claim 12, wherein the torque conversion housing further includes a rotation inertia control device, and the mass distribution of the rotation pin or the torque conversion housing that is eccentric with respect to the center line of the rotation shaft is determined. A continuously variable transmission that is adjusted uniformly.   The continuously variable transmission according to claim 14, wherein the rotary inertia control device is a balance weight.   The continuously variable transmission according to claim 12, wherein the output section includes a driven shaft to which power is transmitted from the rotary pin, a drive shaft that is arranged in parallel to the driven shaft and outputs power, and the driven shaft. A pair of clutch teeth that transmit rotational power in only one direction by a one-way clutch, a rotation tooth that engages with the drive shaft and meshes with one of the pair of clutch teeth, and the drive shaft. A movable tooth that is slid and meshed with or separated from one of the clutch teeth, a fixed tooth that is fixed to the upper shaft, one side meshed with the rotating tooth, and the other side meshed with one of the clutch teeth And a continuously variable transmission.   17. The continuously variable transmission according to claim 16, wherein the link device includes an arm connected to the driven shaft of the power output unit, a rotation of which one side is connected to the arm and the other side is connected to the rotation pin. And a continuously variable transmission.

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