JP2015021558A - Continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a continuously variable transmission capable of suppressing an alignment error of a connecting rod bearing.SOLUTION: A continuously variable transmission includes a lever crank mechanism that converts rotary motion of an input shaft into oscillatory movement of an oscillation link. The lever crank mechanism includes: a cam disc that is eccentrically provided to the input shaft; a rotary disc 6 that is eccentrically provided to the cam disc in a freely rotatable manner; and a connecting rod 15. A ball bearing 16 is arranged between the rotary disc 6 and the connecting rod 15. The ball bearing 16 is made of a rear-joined double row angular ball bearing.

Description

  The present invention relates to a continuously variable transmission of a four-bar linkage mechanism type that can change speed by adjusting a rotation radius with a rotation radius adjustment mechanism provided on a rotation center axis of an input shaft.

  Conventionally, a hollow input shaft that rotates in a case by transmitting a driving force from a main drive source such as an engine provided in a vehicle, an output shaft that is arranged in parallel to the input shaft, and a rotation center axis line A plurality of turning radius adjusting mechanisms provided on the output shaft, a plurality of swing links pivotally supported by the output shaft, and an input side annular portion rotatably fitted to the turning radius adjusting mechanism at one end. A four-bar link mechanism type continuously variable transmission is known that includes a connecting rod connected to the swing end of the swing link at the other end (see, for example, Patent Document 1).

  In the thing of patent document 1, each turning radius adjustment mechanism is eccentric with respect to the rotation center axis line of an input shaft, and the cam part provided in the input shaft, and the rotating part provided eccentrically in this cam part, and was rotatably provided. And a pinion shaft inserted into a hollow input shaft. In addition, a one-way clutch is provided as a one-way rotation prevention mechanism between the swing link and the output shaft.

  The one-way clutch fixes the swing link to the output shaft when the swing link is about to rotate relative to the output shaft, and Spin the swing link idle. A connecting rod bearing is provided between the rotating portion and the input-side annular portion of the connecting rod.

  Each cam portion is provided so as to be positioned in a through hole penetrating in the axial direction of the rotation center axis of the input shaft and in a direction opposite to the eccentric direction with respect to the rotation center axis, and the outer peripheral surface of the cam portion and the through hole are formed. And a notch hole for communication. Further, the cam portion is provided with a pair of expansion portions so as to sandwich the notch hole in the axial direction. The cam portion is connected to the input shaft by spline coupling.

  The input shaft has a hollow shape with one end opened and the other end closed, and a notch hole is provided corresponding to the notch hole of the cam portion. A pinion shaft is inserted into the input shaft. The inserted pinion shaft is exposed from the notch hole of the input shaft and each cam portion. The rotating part is provided with a receiving hole for receiving the camshaft. Internal teeth are formed on the inner peripheral surface of the rotating part that forms the receiving hole.

  The internal teeth mesh with the pinion shaft exposed from the notch hole of the camshaft. When the camshaft and the pinion shaft are rotated at the same speed, the turning radius of the turning radius adjusting mechanism is maintained. When the rotational speeds of the camshaft and the pinion shaft are made different, the rotational radius of the rotational radius adjusting mechanism is changed, and the transmission ratio of the continuously variable transmission is changed.

  When the rotation radius adjustment mechanism is rotated by rotating the input shaft, the rotation radius adjustment mechanism on the input shaft side of the connecting rod rotates to swing the swing link connected to the other end of the connecting rod. The end swings. That is, a lever crank mechanism is configured by the turning radius adjusting mechanism, the connecting rod, and the swing link. Since the swing link is provided on the output shaft via the one-way clutch, the rotational drive force (torque) is transmitted to the output shaft only when rotating to one side.

  The eccentric direction of the cam portion of each turning radius adjusting mechanism is set so as to make a round around the input shaft with different phases. Therefore, the connecting rod that is externally fitted to each turning radius adjusting mechanism causes the swing link to transmit torque to the output shaft in order, so that the output shaft can be smoothly rotated.

JP 2013-19429 A

  In the continuously variable transmission of the four-bar linkage mechanism type, the cam portion is eccentric, and a load from the connecting rod is applied, so that the input shaft is easily bent. When the input shaft is bent, a relative positional shift occurs between the outer ring and the inner ring of the connecting rod bearing, and a straight line (contact straight line) connecting the point where the ball of the connecting rod bearing contacts the outer ring and the point where the ball contacts the inner ring. ) Does not pass through the center of the ball, and alignment error of the connecting rod bearing is likely to occur. When an alignment error of the connecting rod bearing occurs, there is a problem that friction occurs even in a lever crank mechanism that does not transmit driving force.

  An object of this invention is to provide the continuously variable transmission which can suppress the alignment error of a connecting rod bearing in view of the above point.

  [1] In order to achieve the above object, the present invention provides an input shaft that rotates in a case by transmission of a driving force of a main drive source, an output shaft that is arranged in parallel with a rotation center axis of the input shaft, A lever crank mechanism having a swing link pivotally supported by the output shaft, and converting the rotational motion of the input shaft into the swing motion of the swing link; and the swing link to one side with respect to the output shaft The swing link is fixed to the output shaft when trying to rotate relatively, and the swing link is rotated relative to the output shaft when the swing link is rotated relative to the other. And a one-way rotation preventing mechanism that idles the swing link, wherein the lever crank mechanism includes a rotation radius adjustment mechanism capable of adjusting a rotation radius, and a connecting rod that connects the rotation radius adjustment mechanism and the swing link. The turning radius adjuster And a connecting rod between the connecting rod and the connecting rod is a continuously variable transmission, wherein the connecting rod bearing is composed of a back-to-back or front-to-back double row angular contact ball bearing, or a plurality of single rows The angular ball bearing is configured to be back-to-back or front-to-back.

  According to the present invention, a straight line connecting two points where the ball of the connecting rod bearing contacts the outer ring and the inner ring is defined as a contact straight line, and the connecting rod bearing is a back-to-back double-row angular contact ball bearing or a plurality of single-row angular ball bearings. By configuring the row angular contact ball bearings back to back, the two contact straight lines open toward the center line of the connecting rod bearing.

  As a result, even if a load is applied from the connecting rod, the outer ring and the inner ring of the connecting rod bearing are relatively difficult to be displaced. Therefore, according to the continuously variable transmission of the present invention, alignment errors can be prevented or suppressed.

  Further, by configuring the connecting rod bearing as a face-to-face type double-row angular contact ball bearing or a plurality of single-row angular contact ball bearings as face-to-face, the two contact straight lines intersect at or near the center of the connecting rod bearing. can do. Thereby, even if the connecting rod bearing is displaced between the outer ring and the inner ring due to the bending of the input shaft, the angular ball bearing as the connecting rod bearing acts so that the center of the ball is positioned on the contact straight line, Generation of alignment errors can be suppressed.

  [2] Further, as a first specific aspect of the present invention, the connecting rod bearing has an outer ring and is constituted by a back-to-back type double row angular ball bearing, and the outer ring can be constituted by a connecting rod. According to such a configuration, the outer ring of the connecting rod bearing is combined with the input-side annular portion of the connecting rod. Therefore, the number of parts of the continuously variable transmission can be reduced and downsizing can be achieved.

  [3] As a first specific aspect of the present invention, a plurality of lever crank mechanisms are provided, the input shaft is supported by a plurality of input shaft bearings in the case, and the connecting rod bearing includes a ball, an inner ring, A straight line passing through the contact point between the ball and the inner ring and the contact point between the ball and the outer ring is defined as a contact straight line, and the point located at the innermost radial direction of the ball in the radial direction of the connecting rod bearing The straight line that passes through the most radially outward point is defined as the reference straight line, the angle formed by the contact straight line and the reference straight line is defined as the contact angle, and the contact angle of the connecting rod bearing is the same as the input shaft bearing. It can be configured to grow as it approaches.

  Here, the input shaft bends due to an inertial force when the turning radius adjusting mechanism rotates, a load from the connecting rod, or the like. When the input shaft is bent, the portion inclined most with respect to the rotation center axis when the input shaft is not bent is a portion supported by the input shaft bearing. Conversely, at the portion farthest from the input shaft bearing, the inclination angle is substantially parallel to the rotation center axis when the input shaft is not bent.

  Therefore, in the case of a continuously variable transmission including a plurality of lever crank mechanisms, if the contact angle is increased as it approaches the input shaft bearing, the deflection of the input shaft can be suppressed. Thereby, the alignment error of a connecting rod bearing can also be suppressed.

  [4] As a first specific aspect of the present invention, the inner ring can be positioned in the axial direction by a circlip attached to the outer periphery of the turning radius adjusting mechanism. Thereby, the clearance and preload (preload) of a connecting rod bearing can be set appropriately by adjusting the thickness of a circlip.

  [5] Further, as a second specific aspect of the present invention, the connecting rod bearing has an inner ring and is constituted by a face-to-face double row angular contact ball bearing, and the inner ring can be constituted by a turning radius adjusting mechanism. . According to this configuration, the rotating portion also serves as the inner ring of the connecting rod bearing. Therefore, the number of parts of the continuously variable transmission can be reduced, and the radial dimension around the input shaft can be reduced.

  [6] As a second specific aspect of the present invention, the connecting rod bearing has a ball and an outer ring, and has a straight line passing through a contact point between the ball and the inner ring and a contact point between the ball and the outer ring. Defined as a contact straight line, the contact straight line preferably intersects at the center of the connecting rod bearing.

  According to such a configuration, even if the input shaft is bent and curved, the outer ring and the inner ring of the connecting rod bearing are displaced with respect to the center of the connecting rod bearing, and the connecting rod is The position can be shifted to absorb the curvature. At this time, the connecting rod bearing is an angular ball bearing, and even if the outer ring and the inner ring are displaced from each other with the center of the connecting rod bearing as a fulcrum, an increase in friction can be suppressed.

  [7] Also in the second specific embodiment of the present invention, the outer ring may be positioned in the axial direction by a circlip attached to the connecting rod. Thereby, the clearance and preload (preload) of a connecting rod bearing can be set appropriately by adjusting the thickness of a circlip.

Explanatory drawing which shows 1st Embodiment of the power transmission device of this invention in a partial cross section. Explanatory drawing which shows the lever crank mechanism of 1st Embodiment. Explanatory drawing which shows the change of the rotation radius of 1st Embodiment. 3A shows a state where the turning radius is maximum, FIG. 3B shows a case where the turning radius is medium, FIG. 3C shows a case where the turning radius is small, and FIG. 3D shows a state where the turning radius is zero. Explanatory drawing which shows the change of the rocking | fluctuation range of the rocking | fluctuation link with respect to the change of the rotation radius of 1st Embodiment. FIG. 4A shows the swing range when the turning radius is the maximum, FIG. 4B shows the inside of the turning radius, and FIG. 4C shows the swing range when the turning radius is small. FIG. 5A is an explanatory view showing a back-to-back double row angular contact ball bearing of the first embodiment, and FIG. 5B is a partially enlarged view of FIG. 5A. Explanatory drawing which shows the effect | action of the connecting rod bearing of 1st Embodiment. FIG. 7A is an explanatory view showing a face-to-face double row angular contact ball bearing of the second embodiment, and FIG. 7B is a partially enlarged view of FIG. 7A. Explanatory drawing which shows the effect | action of the connecting rod bearing of 2nd Embodiment. FIG. 9A is a cross-sectional view schematically showing a connecting rod bearing according to a second embodiment, FIG. 9A shows a state where the input shaft is desired to be curved, and FIG. 9B is a front-aligned double row angular contact ball bearing where the input shaft is curved. Shows a state in which alignment errors are absorbed.

[First Embodiment]
A first embodiment of a four-bar linkage type continuously variable transmission according to the present invention will be described with reference to FIGS. The continuously variable transmission according to the present embodiment is a transmission capable of setting the speed ratio h (h = rotational speed of the input shaft / rotational speed of the output shaft) to infinity (∞) and the rotational speed of the output shaft to “0”. It is a kind of so-called IVT (Infinity Variable Transmission).

  Referring to FIG. 1, a continuously variable transmission 1 of a four-bar linkage mechanism type rotates about a rotation center axis P1 by receiving a rotational drive force from a main drive source ENG such as an engine or an electric motor that is an internal combustion engine. An output shaft 3 disposed parallel to the rotation center axis P1 and transmitting rotational power to drive wheels (not shown) of the vehicle via a differential gear (not shown), and the rotation center axis P1 And six turning radius adjusting mechanisms 4 provided on the head. A propeller shaft may be provided instead of the differential gear.

  1 and 2, each turning radius adjusting mechanism 4 includes a cam disk 5 as a cam part and a rotating disk 6 as a rotating part. The cam disks 5 have a disk shape, are eccentric from the rotation center axis P <b> 1, and are provided in each rotation radius adjustment mechanism 4 so as to form one set with respect to one rotation radius adjustment mechanism 4. . The cam disk 5 is provided with a through hole 5a penetrating in the direction of the rotation center axis P1. Further, the cam disk 5 is opened in a direction opposite to the direction decentered with respect to the rotation center axis P1, and a notch hole 5b for communicating the outer peripheral surface of the cam disk 5 with the inner peripheral surface constituting the through hole 5a. Is provided.

  Each set of cam disks 5 is arranged so as to make a round in the circumferential direction of the rotation center axis P <b> 1 with six sets of cam disks 5 with a phase difference of 60 degrees.

  The cam disk 5 is formed integrally with the cam disk 5 of the adjacent turning radius adjusting mechanism 4 to constitute an integrated cam portion 5c. The integrated cam portion 5c may be formed by integral molding, or may be integrated by welding two cam portions. A pair of cam disks 5 of each turning radius adjusting mechanism 4 are fixed by bolts (not shown). The cam disk 5 located on the most main drive source side on the rotation center axis P1 is formed integrally with the input shaft end 2a. In this way, the input shaft 2 including the cam disk 5 is configured by the input shaft end portion 2 a and the plurality of cam disks 5.

  The input shaft 2 includes an insertion hole 60 formed by connecting the through holes 5 a of the cam disk 5. Thereby, the input shaft 2 is configured in a hollow shaft shape in which one end opposite to the main drive source ENG is open and the other end is closed. The cam disk 5 located at the other end on the main drive source side is formed integrally with the input shaft end 2a. As a method of integrally forming the cam disk 5 and the input shaft end 2a, integral molding may be used, or the cam disk 5 and the input shaft end 2a may be integrated by welding. .

  Each set of cam disks 5 is rotatably fitted with a disk-shaped rotating disk 6 having a receiving hole 6a for receiving the cam disk 5 in an eccentric state.

  As shown in FIG. 2, the rotating disk 6 has a cam disk 5 center point P2 and a rotating disk 6 center point P3, a distance Ra between the rotation center axis P1 and the center point P2, and the center point P2 and the center point. It is eccentric with respect to the cam disk 5 so that the distance Rb of P3 is the same.

  The receiving hole 6 a of the rotating disk 6 is provided with internal teeth 6 b that are positioned between the pair of cam disks 5.

  In the insertion hole 60 of the input shaft 2, the pinion 7 is positioned so as to be concentric with the rotation center axis P <b> 1 and corresponding to the inner teeth 6 b of the rotating disk 6, and the pinion 7 rotates relative to the input shaft 2 including the cam disk 5. It is arranged to be free. The pinion 7 is formed integrally with a pinion shaft that supports the pinion 7. The pinion 7 may be configured separately from the pinion shaft, and the pinion 7 may be connected to the pinion shaft 2 by spline coupling.

  The pinion 7 meshes with the internal teeth 6 b of the rotating disk 6 through the notch hole 5 b of the cam disk 5. A pinion bearing 7b is provided between the teeth 7a of the pinion 7 adjacent in the axial direction. The pinion 7 supports the input shaft 2 including the cam disk 5 through the pinion bearing 7b. A differential mechanism 8 composed of a planetary gear mechanism or the like is connected to the pinion 7. The driving force of the adjusting drive source 14 is transmitted to the pinion 7 via the differential mechanism 8.

  Since the rotating disk 6 is eccentric with respect to the cam disk 5 such that the distance Ra and the distance Rb are the same, the center point P3 of the rotating disk 6 is positioned on the same axis as the rotation center axis P1. Thus, the distance between the rotation center axis P1 and the center point P3, that is, the eccentricity R1 can be set to “0”.

  The peripheral edge of the rotary disk 6 is provided with a large-diameter input-side annular portion 15a at one end (on the input shaft 2 side), and at the other end (output shaft 3 side) at the end of the input-side annular portion 15a. Two connecting-side annular portions 15a of the connecting rod 15 having a small-diameter output-side annular portion 15b are externally fitted so as to be rotatable through a ball bearing 16 as a pair of connecting rod bearings arranged in the axial direction. Six swing links 18 corresponding to the connecting rod 15 are provided on the output shaft 3 via a one-way clutch 17.

  The one-way clutch 17 is provided between the swing link 18 and the output shaft 3. When the swing link 18 is about to rotate relative to the output shaft 3 on one side, the swing link 18 is connected to the output shaft. 3 (fixed state), and the rocking link 18 is idled with respect to the output shaft 3 (idle state) when trying to rotate relatively to the other side.

  The swing link 18 is formed in an annular shape, and a swing end portion 18 a connected to the output-side annular portion 15 b of the connecting rod 15 is provided below the swing link 18. The swing end portion 18a is provided with a pair of projecting pieces 18b projecting so as to sandwich the output-side annular portion 15b in the axial direction. The pair of projecting pieces 18b are provided with insertion holes 18c corresponding to the inner diameter of the output-side annular portion 15b. A connecting pin 19 as a swing shaft is inserted into the insertion hole 18c and the output side annular portion 15b. Thereby, the connecting rod 15 and the swing link 18 are connected.

  In the present embodiment, the oscillating end 18a is disposed below the output shaft 3 so that the oscillating end 18a of the oscillating link 18 is immersed in the oil reservoir of lubricating oil collected below the case 80. Has been. As a result, the oscillating end 18a can be lubricated with the oil reservoir, and the lubricating oil in the oil reservoir can be lifted by the oscillating motion of the oscillating link 18 to lubricate other components of the continuously variable transmission 1. it can.

  In the description of the embodiment, the gear ratio is defined as the rotational speed of the input shaft / the rotational speed of the output shaft.

  FIG. 3 shows the positional relationship between the pinion shaft 72 and the rotating disk 6 in a state where the eccentric amount R1 (rotating radius) of the rotating radius adjusting mechanism 4 is changed. FIG. 3A shows a state where the eccentric amount R1 is “maximum”, and the pinion shaft is such that the rotation center axis P1, the center point P2 of the cam disk 5, and the center point P3 of the rotation disk 6 are aligned. 72 and the rotary disk 6 are located. At this time, the gear ratio h is minimized.

  FIG. 3B shows a state in which the eccentric amount R1 is set to “medium” which is smaller than that in FIG. 3A, and FIG. The gear ratio h is “medium” which is larger than the gear ratio h in FIG. 3A in FIG. 3B and “large” which is larger than the gear ratio h in FIG. 3B in FIG. FIG. 3D shows a state where the amount of eccentricity R1 is “0”, and the rotation center axis P1 and the center point P3 of the rotating disk 6 are located concentrically. The gear ratio h at this time is infinite (∞). In the continuously variable transmission 1 of the embodiment, the rotational radius of the rotational radius adjusting mechanism 4 is adjustable by changing the eccentric amount R1 by the rotational radius adjusting mechanism 4.

  FIG. 4 shows a change in the swing range of the swing link 18 when the eccentric amount R1 of the turning radius adjusting mechanism 4 is changed. 4A shows the swing range of the swing link 18 when the eccentric amount R1 is the maximum, FIG. 4B shows the swing range of the swing link 18 when the eccentric amount R1 is medium, and FIG. The swing range of the swing link 18 when the eccentric amount R1 is small is shown. It can be seen from FIG. 4 that the swing range becomes narrower as the eccentric amount R1 becomes smaller. When the eccentric amount R1 becomes “0”, the swing link 18 does not swing.

  In the present embodiment, the turning radius adjusting mechanism 4, the connecting rod 15, and the swing link 18 constitute a lever crank mechanism 20 (four-bar linkage mechanism). Then, the lever crank mechanism 20 converts the rotational motion of the input shaft 2 into the swing motion of the swing link 18. The continuously variable transmission 1 of this embodiment includes a total of six lever crank mechanisms 20. When the input shaft 2 is rotated and the pinion shaft 72 is rotated at the same speed as the input shaft 2 when the eccentric amount R1 is not “0”, each connecting rod 15 changes its phase by 60 degrees, and the eccentric amount R1. Accordingly, the swing link 18 swings between the input shaft 2 and the output shaft 3 by alternately pushing the swing end 18a toward the output shaft 3 or pulling it toward the input shaft 2 side.

  Since the output side annular portion 15b of the connecting rod 15 is connected to a swing link 18 provided on the output shaft 3 via a one-way clutch 17, the swing link 18 is pushed and pulled by the connecting rod 15 to swing. Then, the output shaft 3 rotates only when the swing link 18 rotates in either the pushing direction side or the pulling direction side, and the output shaft 3 rotates when the swing link 18 rotates in the other direction. Thus, the force of the swing motion of the swing link 18 is not transmitted to the swing link 18, and the swing link 18 is idled. Since each turning radius adjusting mechanism 4 is arranged with a phase changed every 60 degrees, the output shaft 3 is rotated in turn by each turning radius adjusting mechanism 4.

  In addition, the power transmission device of the present embodiment includes a control unit (not shown) that controls the adjustment drive source 14. The control unit is an electronic unit composed of a CPU, a memory, and the like, and the control program stored in the memory is executed by the CPU, thereby controlling the adjustment drive source 14 and the amount of eccentricity of the turning radius adjustment mechanism 4. It functions to regulate R1.

  Next, with reference to FIG. 5, the ball bearing 16 arrange | positioned between the rotating disk 6 of 1st Embodiment and the input side annular part 15a of the connecting rod 15 is demonstrated in detail. In the drawings of the first embodiment, the cage for the ball bearing 16 is omitted. First, for convenience of explanation, the six lever crank mechanisms 20 shown in FIG. 1 are defined as first to sixth lever crank mechanisms 20 in order from the left.

  Further, a straight line connecting two points, that is, a point where the ball 16a of the ball bearing 16 as the connecting rod bearing and the input side annular portion 15a as the outer ring contact and a point where the ball 16a and the inner ring 16b contact with each other, is a contact straight line (FIG. 5). ). Further, in the radial direction of the ball bearing 16, a straight line (including a straight line parallel to the straight line) passing through a point located at the innermost side of the ball 16a and a point located at the outermost side of the ball 16a is used as a reference straight line (in FIG. 2).

  As shown in FIG. 5, the ball bearing 16 is a back-to-back double row angular contact ball bearing. As a result, the two contact straight lines spread toward the center line of the ball bearing 16 (same as the center P3 of the rotating disk 6). Accordingly, the distance L between the operating points shown in FIG. 5A is larger than that of a deep groove ball bearing or the like, and the positions of the input side annular portion 15a as the outer ring of the ball bearing 16 and the inner ring 16b are not easily displaced. It becomes difficult to multiply errors. In addition, (theta) b of FIG. 5B shows a contact angle.

  Further, as shown in FIG. 6, the closer to the input shaft bearing 2 b that supports the input shaft 2, the more the turning radius adjustment mechanism 4 is inclined.

  Therefore, in the lever crank mechanism 20 of the first embodiment, the lever crank mechanism 20 positioned closer to the input shaft bearing 2b that supports the input shaft 2 is configured to increase the contact angle θ of the ball bearing 16. . Specifically, the lever crank mechanism 20 is configured so that the contact angle θb increases in the order of 3 <2 <first order and the contact angle θb increases in the order of 4 <5 <6th order. Is configured.

  Further, when the input shaft 2 is curved, the ball bearing 16 is constituted by a back-to-back type double row angular ball bearing and has a structure that hardly causes an alignment error. The end of is going to open like a fan. However, the connecting rod 15 contacts the protrusion 18b of the swing link 18 and receives a reaction force that suppresses the force to open the fan 18 from the protrusion 18b. Further, since the connecting pin 19 is inserted into the output-side annular portion 15 b of the connecting rod 15, the connecting pin 19 also receives a reaction force that suppresses the force of opening in a fan shape.

  Therefore, according to the continuously variable transmission 1 of the first embodiment, the force that the input shaft 2 tends to bend due to the reaction force from the swing link 18 and the connecting pin 19 can be suppressed.

  Here, a straight line passing through a contact point between the ball 16a of the ball bearing 16 and the inner ring 16b and a contact point between the ball 16a and the input side annular portion 15a as the outer ring is a contact straight line (indicated by a one-dot chain line in FIG. 5). Define. Further, in the radial direction of the ball bearing 16 as the connecting rod bearing, a straight line (or a straight line parallel to this straight line) passing through the point located at the innermost side and the point located at the outermost side of the ball 16a is a reference straight line ( It is defined as (indicated by a two-dot chain line in FIG. 5). Further, an angle formed by the contact straight line and the reference straight line is defined as a contact angle θ.

  Further, as shown in FIG. 5B, the ball bearing 16 formed of a back-to-back type double row angular contact ball bearing includes a pair of inner rings 16b and 16b. An annular groove 6 c is provided on the outer peripheral surface of the rotating disk 6. A circlip 16c is attached to the annular groove 6c. The circlip 16c is used for positioning the ball bearing 16 in the axial direction of the inner ring 16b.

  In the continuously variable transmission 1 of the first embodiment, the clearance and the preload (preload) between the inner ring 16b of the ball bearing 16 and the ball 16a are appropriately adjusted by selecting a circlip 16c having an appropriate thickness. can do.

  In addition, although the ball bearing 16 of 1st Embodiment demonstrated what was comprised with the back-to-back type double row angular contact ball bearing, this invention is not restricted to this, For example, it comprises with a back-to-back single-row angular contact ball bearing. May be.

  Moreover, in 1st Embodiment, what comprised the ball bearing 16 of all the 1st-6th lever crank mechanisms by the back-to-back type double row angular contact ball bearing was demonstrated. However, the present invention is not limited to this, and only those close to the input shaft bearing 2b may be angular ball bearings.

  Specifically, only the ball bearings 16 of the first, second, fifth, and sixth lever crank mechanisms from the left in FIG. 1 of the first embodiment are constituted by angular ball bearings having the same contact angle θ, and input. The third and fourth ball bearings located in the central part of the two bearings of the shaft may be constituted by ordinary deep groove ball bearings.

  Even in this case, the contact angle θ of the third and fourth ball bearings is set to zero, and the contact angle θ of the other ball bearings is set to a value exceeding zero, and the closer to the input shaft bearing 2b. The configuration is such that the contact angle θ is increased.

  Moreover, in 1st Embodiment, the input side annular part 15a of the connecting rod 15 demonstrated what also had the outer ring | wheel of the ball bearing 16. As shown in FIG. However, the continuously variable transmission of the present invention is not limited to this. For example, although the radial dimension around the input shaft 2 may increase, the ball bearing 16 includes an outer ring separate from the input-side annular portion 15a. It may be.

  In the present embodiment, the input shaft end portion 2 a and the plurality of cam disks 5 constitute the input shaft 2, and the input shaft 2 is formed by connecting the through holes 5 a of the cam disk 5. Explained what provided. However, the input shaft of the present invention is not limited to this. For example, as a component of the input shaft 2, a hollow input shaft core portion having an insertion hole whose one end is open and the other end is closed is provided. A plurality of cam disks are formed by forming a through hole larger than that of the first embodiment so that the input shaft core portion can be inserted into the cam disk, and by connecting each cam disk 5 to the outer peripheral surface of the input shaft core portion by spline. An input shaft may be configured.

  In this case, the hollow input shaft core portion is provided with a notch hole corresponding to the notch hole of the cam disk. Then, the pinion inserted into the input shaft core part meshes with the internal teeth of the rotating disk via the notch hole of the input shaft core part and the notch hole of the cam disk.

  In the present embodiment, the one-way clutch 17 is used as the one-way rotation prevention mechanism. However, the one-way rotation prevention mechanism of the present invention is not limited to this, and torque is applied from the swing link 18 to the output shaft 3. You may comprise with the two-way clutch comprised so that the rotation direction with respect to the output shaft 3 of the rocking | fluctuation link 18 which can be transmitted is switchable.

[Second Embodiment]
Next, a continuously variable transmission 1 according to a second embodiment of the present invention will be described with reference to FIGS. The continuously variable transmission 1 of the second embodiment is configured in the same manner as in the first embodiment except that the ball bearing 16 is a front-to-back type double-row angular contact ball bearing. The same reference numerals are given and description thereof is omitted.

  As shown in FIG. 7, the ball bearing 16 of the second embodiment is a face-to-face double row angular contact ball bearing.

  Each ball bearing 16 includes a pair of outer rings 16d and 16d. Further, the inner ring of the ball bearing 16 of the second embodiment is the rotating disk 6. Thereby, the number of parts can be reduced and the radial dimension around the input shaft 2 can be reduced.

  An annular groove 15 c is provided on the inner peripheral surface of the input side annular portion 15 a of the connecting rod 15. A circlip 16c is attached to the annular groove 15c. The circlip 16c is used for positioning the ball bearing 16 in the axial direction of the outer ring 16d.

  In the continuously variable transmission 1 of the second embodiment, the clearance and preload (preload) between the outer ring 16d of the ball bearing 16 and the ball 16a are appropriately adjusted by selecting a circlip 16c having an appropriate thickness. can do.

  Here, a straight line passing through a contact point between the ball 16a and the outer peripheral surface of the rotating disk 6 as an inner ring and a contact point between the ball 16a and the outer ring 16d is defined as a contact straight line (a chain line in FIG. 7). Further, in the radial direction of the ball bearing 16 as the connecting rod bearing, a straight line (or a straight line parallel to the straight line) passing through the point located at the innermost side of the ball 16a and the point located at the outermost side of the ball 16a. It is defined as a reference straight line (two-dot chain line in FIG. 7). Further, an angle formed by the contact straight line and the reference straight line is defined as a contact angle θb.

  Each contact angle θ of the ball bearing 16 is set so that the contact straight line intersects with the center line of the ball bearing 16 (same as P3 which is the center point of the rotating disk 6).

  According to the continuously variable transmission 1 of the second embodiment, even if the input shaft 2 is bent and curved by a load received from the turning radius adjusting mechanism 4 or the connecting rod 15, as shown in FIG. The position of the outer ring 16d with respect to the rotating disk 6 is twisted about the center of the ball bearing 16 (the center point P3 of the rotating disk 6). The ball bearing 16 is a front-to-back double row angular contact ball bearing in which a contact angle θ is set so that the contact straight line intersects at the center point P3 of the rotating disk 6.

  For this reason, even if the position of the outer ring 16d relative to the rotating disk 6 as the inner ring is twisted about the center point P3 of the rotating disk 6, the center of the ball 16a can be positioned on the contact straight line.

  As a result, the connecting rod 15 can be displaced with respect to the cam disk 5 so as to absorb the curvature of the input shaft 2. Therefore, in the continuously variable transmission 1 of the second embodiment, the occurrence of alignment errors in the ball bearing 16 is suppressed, and the friction of the ball bearing 16 is increased due to the deflection of the input shaft 2 in the lever crank mechanism 20 that is not transmitting power. Can be suppressed.

  In addition, although the ball bearing 16 of 2nd Embodiment demonstrated what comprised the front-alignment type double-row angular contact ball bearing, this invention is not limited to this, For example, it comprises a front-alignment single-row angular contact ball bearing. May be.

  Moreover, in 2nd Embodiment, what comprised the ball bearing 16 of all the lever crank mechanisms with the double-row angular contact ball bearing of the face-to-face type was demonstrated. However, the present invention is not limited to this, and only an angular ball bearing close to the input shaft bearing may be used.

  Specifically, only the ball bearings 16 of the first, second, fifth and sixth lever crank mechanisms from the left in FIG. 1 are composed of angular ball bearings having the same contact angle θ, and two bearings of the input shaft are provided. The third and fourth ball bearings located in the central part of each may be formed of ordinary deep groove ball bearings.

  Even in this case, the contact angle θb of the third and fourth ball bearings is set to zero, and the contact angle θb of the other ball bearings is set to a value exceeding zero, and the closer to the input shaft bearing 2b. The configuration is such that the contact angle θb is increased.

  In the present embodiment, the input shaft end portion 2 a and the plurality of cam disks 5 constitute the input shaft 2, and the input shaft 2 is formed by connecting the through holes 5 a of the cam disk 5. Explained what provided. However, the input shaft of the present invention is not limited to this. For example, as a component of the input shaft 2, a hollow input shaft core portion having an insertion hole whose one end is open and the other end is closed is provided. A plurality of cam disks are formed by forming a through hole larger than that of the second embodiment so that the input shaft core portion can be inserted into the cam disk, and by connecting each cam disk 5 to the outer peripheral surface of the input shaft core portion by spline. An input shaft may be configured.

  In this case, the hollow input shaft core portion is provided with a notch hole corresponding to the notch hole of the cam disk. Then, the pinion inserted into the input shaft core part meshes with the internal teeth of the rotating disk via the notch hole of the input shaft core part and the notch hole of the cam disk.

  In the present embodiment, the one-way clutch 17 is used as the one-way rotation prevention mechanism. However, the one-way rotation prevention mechanism of the present invention is not limited to this, and torque is applied from the swing link 18 to the output shaft 3. You may comprise with the two-way clutch comprised so that the rotation direction with respect to the output shaft 3 of the rocking | fluctuation link 18 which can be transmitted is switchable.

1 continuously variable transmission 2 input shaft 2a input shaft end 2b input shaft bearing 3 output shaft 3a output shaft bearing 4 turning radius adjusting mechanism 5 cam disk (cam portion)
5a Through-hole 5b Notch hole 5c Integral cam part 6 Rotating disc
6a Receiving hole (inner circumference)
6b Inner teeth 7 Pinion 7a Pinion teeth 7b Pinion bearing 8 Differential mechanism (planetary gear mechanism)
12 Stepped pinion 14 Adjustment drive source (motor)
15 connecting rod 15a input side annular portion 15b output side annular portion 16 connecting rod bearing 16a ball 16b inner ring (first embodiment)
16c circlip 16d outer ring (second embodiment)
17 One-way clutch 18 Swing link 18a Swing end 18b Projection piece 18c Insertion hole 19 Connection pin 20 Lever crank mechanism (four-bar link mechanism)
40 control unit 41 input side rotational speed detection unit 42 output side rotational speed detection unit 43 throttle valve opening degree detection unit 60 insertion hole 65 driving wheel 80 case 100 region determination unit 110 target radius setting unit 120 target driving force setting unit 130 diameter reduction Force determination unit 140 Transmission method determination unit 150 Rotational radius difference determination unit 160 Current driving force determination unit P1 Rotation center axis P2 Center point P3 of the cam disk Distance Rb between the center points Ra P1 and P2 of the rotation disk P1 and distance R1 between P2 and P3 Eccentricity Amount (distance between P1 and P3)
θb Contact angle

Claims (7)

An input shaft that rotates in the case by transmission of the driving force of the main drive source,
An output shaft disposed parallel to the rotation center axis of the input shaft;
A lever crank mechanism having a swing link supported by the output shaft, and converting the rotational motion of the input shaft into the swing motion of the swing link;
When the swing link is about to rotate relative to the output shaft, the swing link is fixed to the output shaft, and the swing link is relative to the other relative to the output shaft. A one-way rotation prevention mechanism that idles the swing link with respect to the output shaft when attempting to rotate,
The lever crank mechanism includes a turning radius adjusting mechanism capable of adjusting a turning radius, and a connecting rod connecting the turning radius adjusting mechanism and the swing link,
A continuously variable transmission in which a connecting rod bearing is disposed between the turning radius adjusting mechanism and the connecting rod,
The connecting rod bearing is constituted by a back-to-back type or front-to-face type double-row angular contact ball bearing, or a plurality of single-row angular contact ball bearings that are back-to-back or face-to-face aligned. The continuously variable transmission according to claim 1,
The connecting rod bearing has an outer ring and is composed of a back-to-back double row angular contact ball bearing,
The continuously variable transmission is characterized in that the outer ring is constituted by the connecting rod. A continuously variable transmission according to claim 2,
A plurality of lever crank mechanisms are provided,
The input shaft is supported by a plurality of input shaft bearings in the case,
The connecting rod bearing has a ball and an inner ring, and a straight line passing through a contact point between the ball and the inner ring and a contact point between the ball and the outer ring is defined as a contact straight line, and the diameter of the connecting rod bearing In the direction, a straight line passing through the innermost point and the outermost point of the ball is defined as a reference straight line, and an angle formed by the contact straight line and the reference straight line is defined as a contact angle. And
The continuously variable transmission according to claim 1, wherein a contact angle of the connecting rod bearing is configured to increase as approaching the input shaft bearing. The continuously variable transmission according to any one of claims 1 to 3,
The connecting rod bearing has an inner ring,
The continuously variable transmission is characterized in that the inner ring is axially positioned by a circlip attached to the outer periphery of the turning radius adjusting mechanism. The continuously variable transmission according to claim 1,
The connecting rod bearing has an inner ring and is composed of a face-to-face double row angular contact ball bearing,
The continuously variable transmission is characterized in that the inner ring is constituted by the turning radius adjusting mechanism. The continuously variable transmission according to claim 5,
The connecting rod bearing has a ball and an outer ring,
A straight line passing through a contact point between the ball and the inner ring and a contact point between the ball and the outer ring is defined as a contact straight line,
The continuously variable transmission, wherein the contact straight line intersects at the center of the connecting rod bearing. A continuously variable transmission according to claim 1 or claim 5 or claim 6,
The connecting rod bearing has an outer ring,
The continuously variable transmission is characterized in that the outer ring is axially positioned by a circlip attached to the connecting rod.