JP2015172377A - Belt continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a belt continuously variable transmission capable of suppressing delay in the movement of a variable sheave and facilitating actuator assembly work.SOLUTION: A first pin 44 and a second pin 45 are provided on an output shaft, a fork section 53 of an arm is held between the first pin 44 and the second pin 45, and the movement of the output shaft is transmitted to the arm via one of the first pin 44 and the second pin 45. That is, the output shaft is engaged with the arm only by the first pin 44 and the second pin 45 and clearances that may be present between the output shaft and the arm are reduced to one portion. Since the clearances present between the output shaft and the arm are reduced to one portion, it is possible to greatly suppress a delay in the movement of a variable sheave. Furthermore, the output shaft can be engaged with the arm only by inserting the fork section 53 between the first pin 44 and the second pin 45 and the insertion depth of the arm has less influences on the movement of the output shaft. It is, therefore, possible to greatly facilitate actuator assembly work.

Description

  The present invention relates to a belt-type continuously variable transmission including an actuator that moves a movable sheave.

  Various structures have been proposed for a transmission that moderately changes the output rotation of an engine and transmits it to drive wheels. In particular, in recent years, belt-type continuously variable transmissions have become widespread. The belt-type continuously variable transmission has a driving pulley, a driven pulley, and a belt as basic elements, and the driving pulley and the driven pulley each include a fixed sheave and a movable sheave. As an example of such a belt-type continuously variable transmission, for example, Patent Document 1 discloses a technique for moving a movable sheave by an actuator (see Patent Document 1 (FIG. 13)).

  In the belt-type continuously variable transmission of Patent Document 1, an output rod (91) and a movable sheave (62) of an actuator (90) (the numbers in parentheses indicate the symbols described in Patent Document 1. The same applies hereinafter). The bearing (64), the arm part (82) and the connecting member (130) are mechanically connected.

  Specifically, the arm portion (82) is attached to the outer ring of the bearing (64), the connecting member (130) is connected to the arm portion (82) via the pin (84), and the output rod (91) is connected. It is connected to a connecting member (130) via a pin (132).

  Here, the engagement between the output rod (91) and the connecting member (130) employs a structure in which the pin (132) is fitted into the U groove (131), and therefore the pin to the U groove (131). If the fitting position of (132) becomes too deep, an excessive force is applied to the output rod (91), and the smooth movement of the output rod (91) is hindered. Therefore, attention is required for the assembly work of the actuator (90).

  Further, there is a slight gap for inserting the pin (84) between the pin (84) and the connecting member (130). Similarly, a slight gap exists between the pin (132) and the U groove (131). Therefore, when the output rod (91) starts to move, the connecting member (130) starts moving after the gap between the pin (132) and the U groove (131) becomes zero, and then the pin ( 84) and the connecting member (130), the arm portion (82) starts moving after the gap between them becomes zero. That is, since there are a plurality of gaps in the structure of Patent Document 1, there is a delay from when the actuator (90) is operated until the movable sheave (62) starts moving.

  Furthermore, in the structure of Patent Document 1, since the belt (53) and the pin (132) overlap in the drawing front and back direction, the winding radius of the belt (53) changes and the belt (53) is in the drawing front and back direction. It is necessary to adopt a structure in which the pin (132) and the belt (53) do not come into contact with each other even when moved. However, such a structure makes it difficult to reduce the size of the transmission.

JP 2012-47292 A

  It is an object of the present invention to provide a belt type continuously variable transmission that suppresses a movement delay of a movable sheave and facilitates an assembly operation of an actuator.

The invention according to claim 1 is a fixed sheave fixed to the pulley shaft, a movable sheave supported by the pulley shaft and movable relative to the fixed sheave, and a winding between the movable sheave and the fixed sheave. A belt to be hung, an arm attached to the movable sheave and extending in a direction crossing the axis of the pulley shaft, an output shaft engaged with the arm and disposed parallel to the axis of the pulley shaft, and the output shaft In a belt-type continuously variable transmission including an actuator that moves the movable sheave through the arm by moving in the axial direction,
The output shaft includes a first pin and a second pin arranged at a predetermined interval in the axial direction. The tip of the arm is sandwiched between the first pin and the second pin. The movement of the output shaft is transmitted to the arm via one of two pins.

  The invention according to claim 2 is characterized in that the axes of the first pin and the second pin intersect with the axis of the output shaft.

  In the invention according to claim 3, the arm is attached to the movable sheave via a bearing having an internal clearance, and the arm is inclined most when the outer ring of the bearing is inclined with respect to the inner ring due to the internal clearance. However, the distance between the first pin and the second pin is set so that a gap is secured between the arm and the first pin or the second pin.

  The invention according to claim 4 is characterized in that the first pin and the second pin are arranged outside the locus of the belt when viewed from the direction perpendicular to the axis of the pulley shaft.

  In the invention according to claim 5, the first pin has two protrusions protruding through the output shaft, and the second pin has two protrusions protruding through the output shaft, The tip of the arm is a bifurcated fork, and the output shaft is sandwiched between the forks.

In the invention according to claim 1, the output shaft includes a first pin and a second pin arranged at predetermined intervals in the axial direction, and the tip of the arm is sandwiched between the first pin and the second pin, The movement of the output shaft is transmitted to the arm through one of the first pin and the second pin. That is, the engagement between the output shaft and the arm is performed only by the first pin or the second pin, and the gap existing between the output shaft and the arm is reduced to one place. As a result, in the conventional structure, there are a plurality of gaps, but in the present invention, the gap is reduced to one place, so that the movement delay of the movable sheave can be significantly suppressed.
In addition, the output shaft and the arm can be engaged simply by inserting the tip of the arm between the first pin and the second pin, and the effect of the insertion depth of the arm on the movement of the output shaft is small. Assembling work can be made extremely easy.

  In the invention according to claim 2, since the axis of the first pin and the second pin intersects with the axis of the output shaft, no bending moment acts on the output shaft even if a reaction force is applied from the arm to the output shaft. As a result, the strength of the output shaft may be designed considering only the axial force, and the output shaft can be reduced in diameter. Also, since no bending moment acts on the output shaft, smooth movement of the output shaft is guaranteed.

  In the invention according to claim 3, since the gap is secured between the arm and the first pin or the second pin even when the arm is most inclined, the first pin and the arm are in any inclination state. There is no simultaneous contact with both of the second pins, so that no excessive force is applied to the output shaft. As a result, smooth movement of the output shaft is guaranteed.

  In the invention according to claim 4, when viewed from the direction perpendicular to the axis of the pulley shaft, since the first pin and the second pin are arranged outside the locus of the belt, there is a concern that the belt contacts the first pin and the second pin. Absent. As a result, the belt can be brought close to the output shaft, and the transmission can be made compact. Moreover, since there is no fear that a belt contacts a 1st pin and a 2nd pin, damage to a belt can be prevented.

  In the invention according to claim 5, since the tip of the arm is a bifurcated fork portion, and the output shaft is sandwiched between the fork portions, the rotation of the output shaft and the rotation of the arm can be prevented. As a result, not only the engagement but also the functions of a plurality of detents can be combined to simplify the structure.

It is principal part sectional drawing of the belt-type continuously variable transmission which concerns on this invention. FIG. 2 is a view taken in the direction of arrow 2 in FIG. 1. FIG. 3 is a sectional view taken along line 3-3 in FIG. 2. It is an effect | action figure of a bearing. It is a figure explaining the space | interval between a 1st pin and a 2nd pin.

  Embodiments of the present invention will be described below with reference to the accompanying drawings.

  As shown in FIG. 1, a belt type continuously variable transmission 10 includes a pulley shaft 12 formed at one end of a crankshaft 11, a drive pulley 13 supported by the pulley shaft 12, and the drive pulley 13 not shown. The basic element is a belt 14 that is stretched around a driven pulley. Further, the drive pulley 13 includes a fixed sheave 15 fixed to the pulley shaft 12 and a movable sheave 16 supported by the pulley shaft 12 and movable relative to the fixed sheave 15. The fixed sheave 15 and the movable sheave 16 A belt 14 is wound around the belt.

  A ramp plate 17 is fixed to the pulley shaft 12 behind the movable sheave 16, and a plurality of centrifugal weights 19 are held between the movable sheave 16 and the ramp plate 17. When the pulley shaft 12 rotates and a centrifugal force corresponding to the rotation speed acts on the centrifugal weight 19, the centrifugal weight 19 moves radially outward along the cam surface 21 of the movable sheave 16, and the movable sheave 16 is fixed to the fixed sheave. Move to 15 side. As a result, the interval between the fixed sheave 15 and the movable sheave 16 is reduced, and the winding radius of the belt 14 is increased.

  In the movable sheave 16, the sliding surface of the belt 14 and the cam surface 21 are formed as separate parts, and an arm 26 is attached to a boss portion 23 between both surfaces via a bearing 24. Furthermore, an output shaft 31 of an actuator 30 that moves the movable sheave 16 in cooperation with the centrifugal weight 19 is engaged with the tip of the arm 26.

  The actuator 30 includes a gear group 33 that transmits the power of the motor 32, a nut member 34 that is rotationally driven via the gear group 33, and an output shaft 31 that converts the rotation of the nut member 34 into a linear motion and outputs it. have. The gear group 33 is composed of a plurality of gears, and the final stage gear 36 is formed integrally with the nut member 34. The gear group 33 and the nut member 34 are accommodated in an actuator case 38.

  The actuator case 38 has a structure that supports the rotating shaft of the gear group 33 and the nut member 34 at both ends, respectively, and includes a first case 41 and a second case 42 made of metal.

  As shown in FIG. 2, a first pin 44 is attached to the tip of the output shaft 31, and a first pin 44 having the same diameter as that of the first pin 44 is located at a predetermined distance L from the first pin 44. Two pins 45 are attached. The tip of the arm 26 is sandwiched between the first pin 44 and the second pin 45, and the movement of the output shaft 31 is transmitted to the arm 26 via one of the first pin 44 or the second pin 45. . That is, in this example, the engagement between the output shaft 31 and the arm 26 is performed only by the first pin 44 or the second pin 45, and the gap existing between the output shaft 31 and the arm 26 is reduced to one place. . As a result, the movement delay of the movable sheave 16 due to the gap can be greatly suppressed.

  Furthermore, the first pin 44 and the second pin 45 are disposed outside the locus of the belt 14 when viewed from the direction perpendicular to the axis of the pulley shaft 12 (see FIG. 1). Thereby, there is no fear that the belt 14 contacts the first pin 44 and the second pin 45, and the belt 14 can be brought close to the output shaft 31, so that the transmission can be made compact. Moreover, since there is no fear that the belt 14 contacts the first pin 44 and the second pin 45, damage to the belt 14 can be prevented.

  The first pin 44 and the second pin 45 are fixed to the output shaft 31 by fitting. However, the method of fixing the first pin 44 and the second pin 45 to the output shaft 31 is not limited to fitting, and may be a mechanical method using screws or the like, or a chemical method using adhesives or the like.

  As shown in FIG. 3, the tip of the output shaft 31 has two flat portions 47 and 48 that are parallel to each other. The second pin 45 penetrates from the flat portion 47 to the flat portion 48, and both ends of the second pin 45 protrude from the flat portions 47 and 48. That is, the 2nd pin 45 has the protrusion parts 51 and 52 up and down. Similarly, the 1st pin 44 also has the protrusion parts 51 and 52 (refer FIG. 2).

  In addition, the first pin 44 and the second pin 45 are penetrated as in this example, and the first pin 44 and the second pin 45 are divided into an upper piece and a lower piece, and the upper piece is fixed to the flat portion 47. At the same time, the lower piece may be fixed to the flat surface portion 48 to form the protruding portions 51 and 52.

  The tip of the arm 26 is a bifurcated fork part 53, and the fork part 53 sandwiches the flat part 47 and the flat part 48. That is, since the output shaft 31 is sandwiched between the forks 53, the output shaft 31 and the arm 26 can be prevented from rotating. As a result, not only the engagement but also the functions of a plurality of detents can be combined to simplify the structure.

  Furthermore, the axis 45a of the second pin 45 intersects with the axis 31a of the output shaft 31 (this axis 31a extends in the front and back direction of the drawing). When the output shaft 31 moves and the fork 53 is pushed to the drawing front side by the second pin 45, a reaction force from the arm 26 to the output shaft 31 is applied to the output shaft 31 side. However, since the axis 45 a of the second pin 45 intersects the axis 31 a of the output shaft 31, no bending moment acts on the output shaft 31. As a result, it is sufficient to design the strength of the output shaft 31 in consideration of only the axial force, and the diameter of the output shaft 31 can be reduced. Further, since no bending moment acts on the output shaft 31, smooth movement of the output shaft 31 is guaranteed.

  Similarly, the axis of the first pin (FIG. 2, reference numeral 44) also intersects the axis 31a of the output shaft 31, and even if the fork portion 53 is pushed by the first pin 44, the bending moment is applied to the output shaft 31. Does not work.

  As shown in FIG. 4A, the bearing 24 mainly includes an inner ring 54, rolling elements 55, and an outer ring 56. Since the rolling element 55 rolls between the inner ring 54 and the outer ring 56 in the bearing 24, an internal clearance of about several tens of μm is provided to reduce friction and heat generation during rolling.

  Due to the presence of the internal clearance, as shown in FIG. 4B, when the inner ring 54 is fixed and a moment is applied to the outer ring 56, play is clogged by the amount of the internal clearance, and the outer ring 56 becomes θ relative to the inner ring 54. Just lean.

In the belt-type continuously variable transmission 10, since the moment acts on the outer ring 56 via the arm 26 as the output rod 31 moves, the arm 26 attached to the outer ring 56 tilts, and as a result, FIG. As shown, the fork 53 is tilted.
Here, the distance L between the first pin 44 and the second pin 45 is the same as that between the fork portion 53 and the fork portion 53 even when the inclination of the fork portion 53 is the maximum θmax (the internal clearance is completely clogged). It was set so that a gap of δ1 was secured between the pin 1 and the pin 44. That is, when the thickness of the fork portion 53 is t, L = (t / cos θmax) + δ1.

  5A shows a state in which the output shaft 31 moves to the right side in FIG. 1 and the movement is transmitted to the fork portion 53 via the second pin 45. In FIG. When 31 moves to the left side, the movement is transmitted to the fork portion 53 via the first pin 44, and the fork portion 53 is inclined by θmax on the opposite side to the state shown in FIG. In this case, a gap of δ1 is secured between the fork portion 53 and the second pin 45.

  That is, a gap δ1 is always ensured between the fork portion 53 and the first pin 44 or the second pin 45, and the first pin 44 and the second pin 45 are in any inclination state. Are not in contact with each other at the same time, so that no excessive force is applied to the output shaft 31. As a result, smooth movement of the output shaft 31 is guaranteed. Note that δ1 is set to about several μm.

  Further, when the actuator 30 is assembled, as shown in FIG. 5B, the fork portion 53 is interposed between the first pin 44 and the second pin 45 in a state where gaps δ2 and δ2 larger than ½δ1 are secured. Can be inserted. As described above, the output shaft 31 and the arm 26 can be engaged only by inserting the fork portion 53 between the first pin 44 and the second pin 45, and the insertion depth of the fork portion 53 is determined by the output shaft. Since the influence on the movement of the actuator 31 is small, the assembling work of the actuator 30 can be very easily performed.

  In this example, the first pin 44 and the second pin 45 have the same diameter. However, the output shaft 31 moves from the arm 26 to the output shaft 31 when the output shaft 31 moves to the right and to the left in FIG. Since the reaction force applied is different, the diameters of the first pin 44 and the second pin 45 may be set according to the magnitude of the reaction force. Thereby, the intensity | strength of the 1st pin 44 and the 2nd pin 45 is securable optimally.

  The present invention is suitable for a belt type continuously variable transmission mounted on a motorcycle.

  DESCRIPTION OF SYMBOLS 10 ... Belt type continuously variable transmission, 12 ... Pulley shaft, 14 ... Belt, 15 ... Fixed sheave, 16 ... Movable sheave, 24 ... Bearing, 26 ... Arm, 30 ... Actuator, 31 ... Output shaft, 31a ... Output shaft Axis, 44 ... first pin, 45 ... second pin, 45a ... second pin axis, 51, 52 ... projection, 53 ... fork, 54 ... inner ring, 55 ... outer ring, L ... first pin and second Spacing between pins, δ1... Gap.

Claims (5)

A fixed sheave fixed to the pulley shaft; a movable sheave supported by the pulley shaft and movable relative to the fixed sheave; a belt wound between the movable sheave and the fixed sheave; and the movable sheave And an arm extending in a direction intersecting with the axis of the pulley shaft, an output shaft engaged with the arm and disposed parallel to the axis of the pulley shaft, and moving the output shaft in the axial direction. In a belt-type continuously variable transmission comprising an actuator that moves the movable sheave through an arm,
The output shaft includes a first pin and a second pin arranged at a predetermined interval in the axial direction. The tip of the arm is sandwiched between the first pin and the second pin. A belt type continuously variable transmission characterized in that the movement of the output shaft is transmitted to the arm via one of two pins.   The belt-type continuously variable transmission according to claim 1, wherein the axes of the first pin and the second pin intersect with the axis of the output shaft. The arm is attached to the movable sheave via a bearing having an internal clearance,
The outer ring of the bearing is inclined with respect to the inner ring due to the internal clearance so that a gap is secured between the arm and the first pin or the second pin even when the arm is inclined most. The belt-type continuously variable transmission according to claim 1 or 2, wherein an interval between the first pin and the second pin is set.   The belt type according to any one of claims 1 to 3, wherein the first pin and the second pin are disposed outside the locus of the belt when viewed from a direction perpendicular to the axis of the pulley shaft. Continuously variable transmission. The first pin has two protrusions protruding through the output shaft, and the second pin has two protrusions protruding through the output shaft,
The belt-type continuously variable transmission according to any one of claims 1 to 4, wherein a tip of the arm is a bifurcated fork portion, and the output shaft is sandwiched between the fork portion.

Images