JP6100609B2 - Continuously variable transmission - Google Patents

Description

  The present invention relates to a continuously variable transmission of a four-bar linkage mechanism type using a lever crank mechanism.

  Conventionally, a continuously variable transmission of a four-bar linkage mechanism type including a hollow input shaft to which driving force from a driving source such as an engine is transmitted, an output shaft arranged in parallel with the input shaft, and a plurality of lever crank mechanisms A machine is known (see, for example, Patent Document 1).

  In the continuously variable transmission described in Patent Document 1, the lever crank mechanism includes a turning radius adjusting mechanism provided to rotate about the input shaft, a swing link supported on the output shaft, and one end. The connecting rod is rotatably connected to the turning radius adjusting mechanism, and the other end is connected to the swinging end of the swinging link.

  Between the swing link and the output shaft, when the swing link is about to rotate to one side around the output shaft, the swing link is fixed with respect to the output shaft and to the other side In addition, a one-way clutch is provided as a one-way rotation prevention mechanism that idles the swing link with respect to the output shaft.

  The turning radius adjustment mechanism is a disc-shaped cam portion that rotates integrally with the input shaft in a state of being eccentric with respect to the input shaft, and a rotation that is rotatable in a state of being eccentric with respect to the cam portion and connected to the connecting rod. And a pinion shaft provided integrally with a plurality of pinions in the axial direction, and an adjustment drive source.

  The rotating part is provided with a receiving hole for receiving the cam part at a position eccentric from the center thereof. In addition, internal teeth are formed on the inner peripheral surface of the receiving hole.

  The pinion shaft is disposed concentrically with the input shaft in the hollow input shaft, and is rotatable relative to the input shaft by a driving force from an adjustment drive source. Further, external teeth are provided on the outer periphery of the pinion shaft.

  By the way, the input shaft is formed with a notch hole that is located in a direction opposite to the eccentric direction of the cam portion with respect to the rotation center axis of the input shaft and communicates the inner peripheral surface with the outer peripheral surface.

  The pinion shaft inserted into the input shaft has external teeth formed on the outer peripheral surface thereof exposed from the notch hole of the input shaft and meshed with the internal teeth formed on the inner peripheral surface of the receiving hole of the rotating portion. To do.

  Therefore, when the rotational speed of the input shaft and the pinion shaft is the same, the radius of the rotational motion of the rotational radius adjustment mechanism is maintained, but when the rotational speed of the input shaft and the pinion shaft is different, the rotational radius adjustment mechanism The radius of the rotational motion of is changed, and the gear ratio is changed.

  In this continuously variable transmission, when the turning radius adjusting mechanism is rotated by rotating the input shaft, one end of the connecting rod rotates and swings connected to the other end of the connecting rod. The link swings. Since the swing link is pivotally supported on the output shaft via the one-way clutch, the rotational driving force (torque) is transmitted to the output shaft only when rotating on one side.

  In addition, the cam portions are set so that the phases are different from each other, and the plurality of cam portions make a round in the circumferential direction of the input shaft. For this reason, the connecting rods externally fitted to the respective turning radius adjusting mechanisms allow the respective oscillating links to transmit torque to the output shaft in order so that the output shaft can be smoothly rotated.

International Publication No. 2013/001859

  In such a continuously variable transmission, the rotating radius adjusting mechanism is inserted into the connecting rod by press-fitting the rotating portion of the rotating radius adjusting mechanism after placing the bearing in the annular portion formed on one side of the connecting rod. It is attached so that it can rotate freely.

  However, the rotating part of the turning radius adjustment mechanism moves in the direction of the rotation axis of the input part due to vibrations etc. generated in the continuously variable transmission, and the connecting part disposed between the rotating part itself and the rotating part and the connecting rod. The bearing may fall off the connecting rod.

  The present invention has been made in view of the above points, and an object of the present invention is to provide a continuously variable transmission that can prevent a rotating portion of a turning radius adjusting mechanism and a connecting rod bearing from falling off a connecting rod. To do.

In order to achieve the above object, a continuously variable transmission according to the present invention includes an input unit to which a driving force of a driving source is transmitted, an output shaft having a rotation center axis parallel to the rotation center axis of the input unit, and a rotation radius. The rotation radius adjustment mechanism that can be rotated integrally with the input unit, the swing link that is pivotally supported by the output shaft, and the adjustment that transmits the driving force for adjusting the rotation radius to the rotation radius adjustment mechanism Lever mechanism, a connecting rod connecting the turning radius adjusting mechanism and the swing link, a lever crank mechanism for converting the rotational motion of the turning radius adjusting mechanism into the swinging motion of the swing link, and the swing link Is fixed to the output shaft when trying to rotate to one side about the rotation center axis of the output shaft, and the swing link is idle to the output shaft when trying to rotate to the other side. With a one-way rotation prevention mechanism The turning radius adjusting mechanism is provided with a cam portion that rotates integrally with the input portion while being eccentric with respect to the rotation center axis of the input portion, and a receiving hole through which the cam portion is inserted at a position eccentric from the center. The connecting rod is an annular part that is fitted on the turning radius adjusting mechanism so that the one end part is rotatable, and the other end part is swung. the continuously variable transmission is rotatably connected to the oscillating end portion of the link, the cam portion may have a extended portion extending in the radial direction so as to prevent axial movement of the rotating part The turning radius adjusting mechanism has a pinion shaft that is transmitted with the cam portion to the receiving hole provided in the rotating portion, and to which the driving force of the adjusting drive source is transmitted. Inner teeth are formed on the inner peripheral surface of the receiving hole. The outer surface of the pinion shaft is formed with external teeth that mesh with the internal teeth. A friction member for reducing the relative rotational speed of the rotating portion and the cam portion is provided between the rotating portion and the extending portion, or a contact portion and / or an extending portion with the extending portion of the rotating portion. of the contact portion between the rotating part, it characterized that you have been friction portion for decelerating the relative rotational speed between the rotary portion and the cam portion is formed.

  According to the present invention, the relative movement in the axial direction of the rotating portion with respect to the cam portion is prevented by the extending portion of the cam portion, so that the rotating portion and the rotating portion that are fitted in the connecting rod from the axial direction. And the connecting rod bearing disposed between the connecting rod and the connecting rod can be prevented from falling off the connecting rod.

Further , when a differential rotation occurs between the rotating portion and the cam portion, the relative rotational speed of both can be reduced by the frictional force. Therefore, the impact when the backlash between the internal teeth and external teeth is clogged due to switching of the contact surface between the internal teeth of the rotating part and the external teeth of the pinion shaft, which occurs due to the mechanism of the lever crank mechanism, is reduced. Accordingly, the rattling noise generated at that time can be reduced.

Sectional drawing which shows the continuously variable transmission of embodiment of this invention. The schematic diagram which shows the turning radius adjustment mechanism, connecting rod, and rocking | fluctuation link of the continuously variable transmission shown in FIG. 1 from an axial direction. It is a schematic diagram which shows the change of the rotation radius of the rotation radius adjustment mechanism of the continuously variable transmission of FIG. 1, (a) is the maximum rotation radius, (b) is a rotation radius inside, (c) is a rotation radius small. , (D) shows a case where the radius of rotation is “0”. FIG. 2 is a schematic diagram showing a relationship between a change in a rotation radius of a rotation radius adjusting mechanism of the continuously variable transmission of FIG. 1 and a swing angle of a swing motion of a swing link, wherein (a) shows a maximum rotation radius; b) shows the swing angle of the swinging motion of the swing link when the rotational radius is medium, and (c) shows the swing angle of the swing link when the rotational radius is small. Sectional drawing which expands and shows the part of the periphery of a pinion shaft arrange | positioned at the continuously variable transmission of FIG. FIG. 2 is a schematic diagram showing the operation of the lever crank mechanism when the eccentricity of the continuously variable transmission of FIG. 1 is not “0”, where (a) shows a state where the swing end is at an external dead center, and (b) shows The state where the swing end is moving from the external dead center to the internal dead center , (c) is the state where the swing end is at the internal dead center, and (d) is the internal end of the swing end. It shows the state in the middle of moving to the external dead center . It is a schematic diagram which shows the contact state of the external teeth of the pinion shaft and the internal teeth of the rotating disk when the load applied to the pinion shaft of the continuously variable transmission of FIG. 1 is reversed. (B) is a state immediately after the applied load is switched from a load in one side direction to a load in the other side direction, and (c) is a load from the load in one side direction to the load in the other side direction. The state after sufficient time has passed since switching.

  Hereinafter, embodiments of the continuously variable transmission of the present invention will be described. The continuously variable transmission of the present embodiment is a four-bar linkage type continuously variable transmission, and outputs with a gear ratio i (i = rotational speed of the input section / rotational speed of the output shaft) set to infinity (∞). This is a kind of transmission that can make the rotational speed of the shaft "0", so-called IVT (Infinity Variable Transmission).

  First, with reference to FIG.1 and FIG.2, the structure of the continuously variable transmission 1 of this embodiment is demonstrated.

  The continuously variable transmission 1 of this embodiment includes an input shaft 2 that is an input unit, an output shaft 3, and six turning radius adjustment mechanisms 4.

  The input shaft 2 is a hollow member, and rotates about the rotation center axis P <b> 1 of the input shaft 2 by receiving a rotational driving force from a driving source such as an internal combustion engine or an electric motor.

  The output shaft 3 is disposed in parallel with the input shaft 2 and transmits rotational power to a drive unit such as a drive wheel of a vehicle via a differential gear, a propeller shaft, and the like (not shown).

  Each of the turning radius adjusting mechanisms 4 is provided so as to rotate about the rotation center axis P1 of the input shaft 2, and includes a cam disk 5 as a cam part, a rotating disk 6 as a rotating part, and a pinion shaft 7. Have.

  The cam disks 5 have a disk shape, and are provided in pairs on the input shaft 2 so as to be eccentric from the rotation center axis P <b> 1 of the input shaft 2 and rotate integrally with the input shaft 2. Each set of cam disks 5 is set so as to have a phase difference of 60 °, and the six sets of cam disks 5 are arranged so as to make a round in the circumferential direction of the input shaft 2.

  The rotating disk 6 has a disk shape in which a receiving hole 6a is provided at a position eccentric from the center thereof, and is rotatably fitted to the cam disk 5 one by one through the receiving hole 6a. doing.

  The center of the receiving hole 6a of the rotating disk 6 is a distance Ra from the rotation center axis P1 of the input shaft 2 to the center P2 of the cam disk 5 (center of the receiving hole 6a) and the center P2 of the cam disk 5 to the rotating disk 6. The distance Rb to the center P3 is the same. The receiving hole 6 a of the rotating disk 6 is provided with an internal tooth 6 b at a position between the pair of cam disks 5.

  The pinion shaft 7 is disposed concentrically with the input shaft 2 in the hollow input shaft 2 and is rotatable relative to the input shaft 2. Further, external teeth 7 a are provided on the outer periphery of the pinion shaft 7. Further, a differential mechanism 8 is connected to the pinion shaft 7.

  By the way, the input shaft 2 has an inner peripheral surface at a position corresponding to the pair of cam disks 5 on a peripheral surface in a direction opposite to the eccentric direction of the cam disk 5 with respect to the rotation center axis P1 of the input shaft 2. And a notch hole 2a is formed to communicate with the outer peripheral surface. The external teeth 7 a provided on the outer periphery of the pinion shaft 7 are meshed with the internal teeth 6 b provided on the inner periphery of the receiving hole 6 a of the rotating disk 6 through the notch hole 2 a of the input shaft 2.

  The differential mechanism 8 is configured as a planetary gear mechanism, and includes a sun gear 9, a first ring gear 10 connected to the input shaft 2, a second ring gear 11 connected to the pinion shaft 7, the sun gear 9 and the first ring gear 10. And a carrier 13 that pivotally supports a stepped pinion 12 including a small-diameter portion 12b meshing with the second ring gear 11 so as to rotate and revolve. The sun gear 9 of the differential mechanism 8 is connected to a rotating shaft 14a of an adjustment drive source 14 composed of an electric motor for the pinion shaft 7.

  Therefore, when the rotational speed of the adjusting drive source 14 is the same as the rotational speed of the input shaft 2, the sun gear 9 and the first ring gear 10 rotate at the same speed, so that the sun gear 9, the first ring gear 10, the second gear The four elements of the ring gear 11 and the carrier 13 are locked so as not to rotate relative to each other, and the pinion shaft 7 connected to the second ring gear 11 rotates at the same speed as the input shaft 2.

  When the rotational speed of the adjusting drive source 14 is made slower than the rotational speed of the input shaft 2, the rotational speed of the sun gear 9 is Ns, the rotational speed of the first ring gear 10 is NR1, and the gear ratio between the sun gear 9 and the first ring gear 10 ( When j is the number of teeth of the first ring gear 10 / the number of teeth of the sun gear 9, the rotation speed of the carrier 13 is (j · NR1 + Ns) / (j + 1). Further, the gear ratio between the sun gear 9 and the second ring gear 11 ((number of teeth of the second ring gear 11 / number of teeth of the sun gear 9) × (number of teeth of the large diameter portion 12a of the stepped pinion 12 / number of teeth of the small diameter portion 12b). ) Is k, the rotation speed of the second ring gear 11 is {j (k + 1) NR1 + (k−j) Ns} / {k (j + 1)}.

  When there is a difference between the rotational speed of the input shaft 2 and the rotational speed of the pinion shaft 7, the rotating disk 6 rotates the periphery of the cam disk 5 around the center P <b> 2 of the cam disk 5.

  As shown in FIG. 2, the rotating disk 6 is eccentric with respect to the cam disk 5 so that the distance Ra from P1 to P2 and the distance Rb from P2 to P3 are the same. Therefore, the center P3 of the rotating disk 6 is positioned on the same line as the rotation center axis P1 of the input shaft 2, and the distance between the rotation center axis P1 of the input shaft 2 and the center P3 of the rotating disk 6, that is, the eccentric amount R1 is set. It can also be set to “0”.

  A connecting rod 15 is rotatably fitted around the periphery of the rotating radius adjusting mechanism 4, specifically, the rotating disk 6 of the rotating radius adjusting mechanism 4.

  The connecting rod 15 has a large-diameter large-diameter annular portion 15a at one end, and a small-diameter annular portion 15b having a smaller diameter than the diameter of the large-diameter annular portion 15a at the other end. The large-diameter annular portion 15a of the connecting rod 15 is externally fitted to the rotary disk 6 via a connecting rod bearing 16 formed of a ball bearing.

  A swing link 18 is pivotally supported on the output shaft 3 via a one-way clutch 17 as a one-way rotation prevention mechanism.

  The one-way clutch 17 fixes the swing link 18 with respect to the output shaft 3 when trying to rotate to one side around the rotation center axis P4 of the output shaft 3, and outputs when trying to rotate to the other side. The swing link 18 is idled with respect to the shaft 3.

  The swing link 18 is provided with a swing end portion 18a, and the swing end portion 18a is provided with a pair of projecting pieces 18b formed so as to sandwich the small-diameter annular portion 15b in the axial direction. Yes. The pair of projecting pieces 18b are formed with through holes 18c corresponding to the inner diameter of the small-diameter annular portion 15b. The connecting rod 15 and the swing link 18 are connected by inserting the connecting pin 19 into the through hole 18c and the small-diameter annular portion 15b.

  In the present embodiment, the input shaft 2 is used as the input unit, but the input unit used in the continuously variable transmission of the present invention is not limited to such an input shaft 2. For example, an input portion configured by providing a cam disk 5 with a through hole and connecting the cam disk 5 in a shaft shape so as to connect the through holes may be used.

  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 used in the continuously variable transmission of the present invention is limited to the one-way clutch 17. Absent. For example, you may comprise with the two-way clutch (two-way clutch) comprised so that switching of the rotation direction with respect to the output shaft 3 of the rocking | fluctuation link 18 which can transmit a torque from the rocking | fluctuation link 18 to the output shaft 3 is possible.

  Next, the lever crank mechanism of the continuously variable transmission according to this embodiment will be described with reference to FIGS.

  As shown in FIG. 2, in the continuously variable transmission 1 of the present embodiment, a lever radius adjusting mechanism 4, a connecting rod 15, and a swing link 18 constitute a lever crank mechanism 20 (four-bar linkage mechanism). ing.

  The lever crank mechanism 20 converts the rotational motion of the input shaft 2 into the swing motion of the swing link 18. As shown in FIG. 1, the continuously variable transmission 1 of this embodiment includes a total of six lever crank mechanisms 20.

  In this lever crank mechanism 20, when the eccentric amount R1 of the turning radius adjusting mechanism 4 is not "0", when the input shaft 2 and the pinion shaft 7 are rotated at the same speed, each connecting rod 15 has a phase of 60 degrees. While changing, the swing link 18 is swung by alternately repeating pushing between the input shaft 2 and the output shaft 3 toward the output shaft 3 and pulling toward the input shaft 2.

  Since the one-way clutch 17 is provided between the swing link 18 and the output shaft 3, the swing link 18 is pushed or pulled and the swing link 18 is swung. The dynamic link 18 is fixed, and the force of the swinging motion of the swinging link 18 is transmitted to the output shaft 3 to rotate the output shaft 3. In the other case, the swinging link 18 is idled to the output shaft 3. The force of the swing motion of the swing link 18 is not transmitted. Since the six turning radius adjusting mechanisms 4 are arranged by changing the phase by 60 degrees, the output shaft 3 is sequentially rotated by the six turning radius adjusting mechanisms 4.

  Moreover, in the continuously variable transmission 1 of this embodiment, as shown in FIG. 3, the rotation radius of the rotation radius adjustment mechanism 4, that is, the eccentric amount R1 is adjustable.

  FIG. 3A shows a state in which the amount of eccentricity R1 is “maximum”, and the rotation center axis P1 of the input shaft 2, the center P2 of the cam disk 5, and the center P3 of the rotation disk 6 are aligned. The pinion shaft 7 and the rotating disk 6 are located. In this case, the gear ratio i 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. 3C illustrates that the eccentric amount R1 is smaller than that in FIG. Is shown. The gear ratio i is “medium” which is larger than the gear ratio i in FIG. 3A in FIG. 3B, and “large” which is larger than the gear ratio i in FIG. 3B in FIG. Become. FIG. 3D shows a state where the amount of eccentricity R1 is “0”, and the rotation center axis P1 of the input shaft 2 and the center P3 of the rotating disk 6 are located concentrically. In this case, the gear ratio i is infinite (∞).

  FIG. 4 is a schematic diagram showing the relationship between the rotation radius of the rotation radius adjusting mechanism 4 of the present embodiment, that is, the change in the eccentricity R1 and the swing angle of the swing motion of the swing link 18.

  4A shows the case where the eccentric amount R1 is “maximum” in FIG. 3A (when the gear ratio i is the minimum), and FIG. 4B shows the case where the eccentric amount R1 is “ 4 (c) shows the case where the eccentric amount R1 is “small” in FIG. 3 (c) (when the gear ratio i is large). The swing range θ2 of the swing link 18 with respect to the rotational movement of the turning radius adjusting mechanism 4 is shown. Here, the distance from the rotation center axis P4 of the output shaft 3 to the connecting point of the connecting rod 15 and the swinging end portion 18a, that is, the center P5 of the connecting pin 19, is the length R2 of the swinging link 18.

  As is apparent from FIG. 4, as the eccentric amount R1 becomes smaller, the swing range θ2 of the swing link 18 becomes narrower, and when the eccentric amount R1 becomes “0”, the swing link 18 swings. Stops moving.

  Next, the configuration of the cam disk 5 of the continuously variable transmission 1 of the present embodiment will be described in detail with reference to FIGS. 2 and 5.

  As shown in FIG. 2, the cam disk 5 has a disk shape, and a through hole 5 a into which the input shaft 2 is inserted and fixed is formed at a position eccentric from the center thereof. Further, as shown in FIG. 5, an annular extending portion 5 b extending in the radial direction is provided on the peripheral edge portion of the cam disk 5.

  As shown in FIG. 5, the cam disks 5 are fitted into the receiving holes 6 a provided in the rotating disk 6 so as to sandwich the rotating disk 6 in pairs as viewed from the axial direction. As a result, the extended portion 5b of the cam disk 5 comes into contact with the area around the receiving hole 6a of the rotating disk 6 so as to be sandwiched from the axial direction, and the relative position in the axial direction of the rotating disk 6 with respect to the cam disk 5 is fixed. .

  As described above, in the continuously variable transmission 1 of the present embodiment, the relative position in the axial direction of the cam disk 5 and the rotary disk 6 is fixed by the extending portion 5 b of the cam disk 5. The rotating disk 6 is difficult to move in the axial direction of the rotation center axis P1 of the input shaft 2.

  Thereby, the positional deviation of the rotating disk 6 in the axial direction can be prevented, and the falling off from the rotating disk 6 itself or the connecting rod bearing 16 disposed between the rotating disk 6 and the connecting rod 15 can be prevented.

  Further, when the roller bearing 21 is disposed between the cam disk 5 and the rotating disk 6, the extension part 5b can prevent the roller bearing 21 from falling off.

  By the way, in the continuously variable transmission 1 of this embodiment, the direction of the load applied to the external teeth 7a of the pinion shaft 7 changes every moment during the operation of the lever crank mechanism 20 due to its mechanism.

  Therefore, a load applied to the pinion shaft 7 during the operation of the lever crank mechanism 20 of the continuously variable transmission 1 of the present embodiment will be described with reference to FIGS. 2 and 6.

  As shown in FIG. 2, the lever crank mechanism 20 of the continuously variable transmission 1 of the present embodiment includes a pinion shaft 7, a turning radius adjusting mechanism 4 having a cam disk 5 and a rotating disk 6, a connecting rod 15, And an oscillating link 18.

  Then, a line (a line having a length Ra) connecting the center P2 of the cam disk and the rotation center axis of the pinion shaft 7, that is, the rotation center axis P1 of the input shaft 2, and the center P2 of the cam disk 5 and the rotation disk 6 A line connecting the center P3 (a line having the length Rb) forms a V shape with the center P2 of the cam disk 5 as an axis.

  This V-shaped opening degree, that is, the angle formed by these two lines changes between 0 ° and 180 ° depending on the relative rotation of the pinion shaft 7 with respect to the input shaft 2.

  Incidentally, during the operation of the lever crank mechanism 20, a load that changes from moment to moment is applied to the center P <b> 3 of the rotating disk 6.

  For example, as shown in FIG. 6A, the center of the swing end 18a of the swing link 18, that is, the center P5 of the connecting pin 19 that connects the swing link 18 and the connecting rod 15 swings. It reaches the position farthest from the input shaft 2 in the swing range of the link 18 (hereinafter referred to as “external dead center”), and the position closest to the input shaft 2 in the swing range of the swing link 18 (hereinafter referred to as “external dead center”). In a state in which movement toward “internal dead center” is started, a V-shape formed by a line having a length Ra and a line having a length Rb is formed from the swing link 18 through the connecting rod 15. A load in the closing direction is applied to the center P3 of the rotating disk 6.

  Thereafter, as shown in FIG. 6B, in the state where the center P5 of the connecting pin 19 reaches an intermediate position between the external dead center and the internal dead center and starts moving toward the internal dead center, The direction of the load applied to the center P3 of the disk 6 is switched, and a load in the direction of opening the V-shape is applied to the center P3 of the rotating disk 6.

  After that, as shown in FIG. 6C, when the center P5 of the connecting pin 19 reaches the inner dead center and starts moving toward the outer dead center, it is added to the center P3 of the rotating disk 6 again. The direction of the load is switched, and a load in the direction of closing the V shape is applied to the center P3 of the rotating disk 6.

Thereafter, as shown in FIG. 6 (d), in the state where the center P5 of the connecting pin 19 reaches an intermediate position between the internal dead center and the external dead center and starts to move toward the external dead center, again, The direction of the load applied to the center P3 of the rotating disk 6 is switched, and a load in the direction of opening the V shape is applied to the center P3 of the rotating disk 6.

  Thereafter, the lever crank mechanism 20 continues to operate by sequentially repeating the states shown in FIGS. 6 (a) to 6 (d).

  The load applied to the center P3 of the rotating disk 6 during the operation of the lever crank mechanism 20 meshes with the inner teeth 6b via the inner teeth 6b formed in the receiving holes 6a provided in the rotating disk 6. It is added to the external teeth 7a of the pinion shaft 7.

  Accordingly, the load applied to the center P3 of the rotating disk 6 is periodically switched during one operation of the lever crank mechanism 20 as described above, so that the direction of the load applied to the pinion shaft 7 is also switched. Become.

  Since a backlash is provided between the external teeth 7a of the pinion shaft 7 and the internal teeth 6b of the rotary disk 6, when the direction of the load is switched, the teeth of the external teeth 7a of the pinion shaft 7 Of the surfaces, the tooth surface on the side that has been in contact with the internal teeth 6b of the rotating disk 6 so far is separated from the internal teeth 6b, and the tooth on the opposite side that has not been in contact with the internal teeth 6b of the rotating disk 6 until then. The surface comes into contact with the internal teeth 6b.

  Therefore, at the time of switching, there is a possibility that a rattling sound is generated due to contact between the external teeth 7a of the pinion shaft 7 and the internal teeth 6b of the rotary disk 6.

  However, in the continuously variable transmission 1 of the present embodiment, as shown in FIG. 5, an annular friction member 22 is provided between the extended portion 5 b of the cam disk 5 and the peripheral portion of the receiving hole 6 a of the rotating disk 6. Is arranged.

  The friction member 22 is made of a material having a higher friction coefficient than the rotating disk 6 and the cam disk 5.

  Since the friction member 22 is provided, the continuously variable transmission 1 according to this embodiment includes the internal teeth 6b of the rotating disk 6 and the external teeth 7a of the pinion shaft 7 that are generated on the lever crank mechanism 20. The impact when the contact surface is switched and the backlash between the inner teeth 6b and the outer teeth 7a is clogged can be reduced, and accordingly, the rattling noise generated at that time can also be reduced.

  Specifically, first, in the state shown in FIG. 7A, that is, in the state where the rotation direction of the rotary disk 6 is one side (clockwise on the paper surface of FIG. 7A), the cam disk 5 is As the rotary disk 6 rotates, the pinion shaft 7 rotates to one side about the rotation center axis line of the pinion shaft 7, that is, the rotation center axis line P1 of the input shaft 2.

  Next, in the state shown in FIG. 7B, in the state immediately after the rotation direction of the rotary disk 6 is switched from one side to the other side (counterclockwise on the paper surface of FIG. 7B), the pinion shaft 7 Of the tooth surfaces of the outer teeth 7a, the tooth surfaces that have been in contact with the inner teeth 6b of the rotating disk 6 so far are separated from the inner teeth 6b, and the tooth surfaces that have not been in contact with the inner teeth 6b of the rotating disk 6 until then. The cam disk 5 and the rotary disk 6 rotate relative to each other until they contact the inner teeth 6b.

  At this time, the speed of the relative rotation is such that the friction member 22 exists between the extension portion 5b of the cam disk 5 and the peripheral portion of the receiving hole 6a of the rotation disk 6, so that the friction member 22 exists. Slower than if not. As a result, compared to the case where the friction member 22 is not provided, the impact caused by the contact between the inner teeth 6b and the outer teeth 7a is alleviated, and consequently the rattling noise caused by the impact is also reduced.

  Thereafter, in the state shown in FIG. 7C, that is, after a sufficient time has passed since the tooth surfaces of the external teeth 7a contacting the internal teeth 6b are switched, the cam disk 5 is rotated by the rotating disk 6. Accordingly, the input shaft 2 rotates around the rotation center axis P1 to the other side.

  Thus, the continuously variable transmission 1 of this embodiment can reduce rattling noise compared to a conventional continuously variable transmission that does not include the extending portion 5b and the friction member 22.

  Moreover, although the said embodiment demonstrated the case where the load applied to the pinion shaft 7 switches by operation | movement of the lever crank mechanism 20, the continuously variable transmission of this invention is not restricted to such a case, For other reasons, the pinion Even when the load applied to the shaft 7 is switched, the rattling noise can be reduced.

  Although the illustrated embodiment has been described above, the present invention is not limited to such a form.

  In the above embodiment, the annular friction member 22 is disposed between the extended portion 5 b of the cam disk 5 and the peripheral portion of the receiving hole 6 a of the rotating disk 6, so that the relative rotation between the cam disk 5 and the rotating disk 6 is achieved. The speed is reduced.

  However, the continuously variable transmission of the present invention is not limited to such a configuration, and is only in a part of the region between the extended portion 5b of the cam disk 5 and the peripheral portion of the receiving hole 6a of the rotating disk 6. A friction member may be arranged.

  Further, a friction member is not disposed, but a contact portion formed on the surface of the extending portion 5b of the cam disc 5 on the rotating disk 6 side or a contact portion formed on the peripheral portion of the receiving hole 6a of the rotating disc 6 is provided. Alternatively, a roughening process may be performed on the contact portion or both contact portions, and a friction portion having an increased friction coefficient in the contact region may be provided.

  In the above embodiment, the extending portion 5b of the cam disk 5 is formed in an annular shape. However, the continuously variable transmission of the present invention is not limited to such a configuration, and the rotating disk extends in the radial direction. Any shape can be used as long as it can contact 6 in the axial direction.

  Further, in the above embodiment, the extending portion 5b is provided in each of the two cam disks 5 for one rotating disk 6, but the continuously variable transmission of the present invention is limited to such a configuration. Instead of this, only one of the two cam disks 5 may be provided with the extending portion 5b.

DESCRIPTION OF SYMBOLS 1 ... Continuously variable transmission, 2 ... Input shaft (input part), 2a ... Notch hole, 3 ... Output shaft, 4 ... Turning radius adjustment mechanism, 5 ... Cam disk (cam part), 5a ... Through-hole, 5b ... Extension Out part, 6 ... rotating disk (rotating part), 6a ... receiving hole, 6b ... internal tooth, 7 ... pinion shaft, 7a ... external tooth, 8 ... differential mechanism, 9 ... sun gear, 10 ... first ring gear, 11 ... Second ring gear, 12 ... Stepped pinion, 12a ... Large diameter part, 12b ... Small diameter part, 13 ... Carrier, 14 ... Adjusting drive source, 14a ... Rotating shaft, 15 ... Connecting rod, 15a ... Large diameter annular part, 15b ... small diameter annular part, 16 ... connecting rod bearing, 17 ... one-way clutch (one-way rotation prevention mechanism), 18 ... swing link, 18a ... swing end, 18b ... projecting piece, 18c ... through hole, 19 ... connection Pin, 20 ... Lever crank mechanism, 21 ... B La bearing, 22 ... friction member, i ... gear ratio, P1 ... rotation center axis of input shaft 2, P2 ... center of cam disk 5, P3 ... center of rotation disk 6, P4 ... rotation center axis of output shaft 3, P5 ... the center of the connecting pin 19, Ra ... the distance between P1 and P2, Rb ... the distance between P2 and P3, the distance between R1 ... P1 and P3 (the amount of eccentricity, the turning radius of the turning radius adjusting mechanism 4), R2 ... the distance between P4 and P5 Distance (length of rocking link 18), θ1: rotation angle of turning radius adjusting mechanism 4, θ2: rocking range of rocking link 18.

Claims (2)

An input unit for transmitting the driving force of the driving source;
An output shaft having a rotation center axis parallel to the rotation center axis of the input unit;
A rotation radius adjustment mechanism that can adjust the rotation radius and that can rotate integrally with the input unit, a swing link that is pivotally supported by the output shaft, and a drive that adjusts the rotation radius to the rotation radius adjustment mechanism. An adjustment drive source for transmitting force; and a connecting rod for connecting the turning radius adjusting mechanism and the swinging link, and converting the rotational motion of the turning radius adjusting mechanism into the swinging motion of the swinging link. A lever crank mechanism,
The swinging link is fixed to the output shaft when the swinging link is about to rotate to one side around the rotation axis of the output shaft, and the output shaft is about to rotate to the other side. A one-way rotation prevention mechanism that idles the swing link,
The turning radius adjusting mechanism includes a cam portion that rotates integrally with the input portion in a state of being eccentric with respect to the rotation center axis of the input portion, and a receiving hole through which the cam portion is inserted at a position that is eccentric from the center. And a rotating part that is rotatable in an eccentric state with respect to the cam part,
The connecting rod is an annular portion having one end portion rotatably fitted to the turning radius adjusting mechanism, and the other end portion is rotatably connected to the swing end portion of the swing link. A step transmission,
The cam unit may have a extended portion extending in the radial direction so as to prevent axial movement of the rotating part,
The turning radius adjusting mechanism includes a pinion shaft to which a driving force of the adjusting driving source is transmitted and inserted into the receiving hole provided in the rotating portion together with the cam portion.
Inner teeth are formed on the inner peripheral surface of the receiving hole, and outer teeth that engage with the inner teeth are formed on the outer peripheral surface of the pinion shaft,
Wherein between the rotating part and the extending portion, the continuously variable transmission, wherein that you have provided a friction member to decelerate the relative rotational speed between the cam portion and the rotating portion. An input unit for transmitting the driving force of the driving source;
An output shaft having a rotation center axis parallel to the rotation center axis of the input unit;
A rotation radius adjustment mechanism that can adjust the rotation radius and that can rotate integrally with the input unit, a swing link that is pivotally supported by the output shaft, and a drive that adjusts the rotation radius to the rotation radius adjustment mechanism. An adjustment drive source for transmitting force; and a connecting rod for connecting the turning radius adjusting mechanism and the swinging link, and converting the rotational motion of the turning radius adjusting mechanism into the swinging motion of the swinging link. A lever crank mechanism,
The swinging link is fixed to the output shaft when the swinging link is about to rotate to one side around the rotation axis of the output shaft, and the output shaft is about to rotate to the other side. A one-way rotation prevention mechanism that idles the swing link,
The turning radius adjusting mechanism includes a cam portion that rotates integrally with the input portion in a state of being eccentric with respect to the rotation center axis of the input portion, and a receiving hole through which the cam portion is inserted at a position that is eccentric from the center. And a rotating part that is rotatable in an eccentric state with respect to the cam part,
The connecting rod is an annular portion having one end portion rotatably fitted to the turning radius adjusting mechanism, and the other end portion is rotatably connected to the swing end portion of the swing link. A step transmission,
The cam portion has an extending portion that extends in a radial direction so as to prevent movement of the rotating portion in the axial direction;
The turning radius adjusting mechanism includes a pinion shaft to which a driving force of the adjusting driving source is transmitted and inserted into the receiving hole provided in the rotating portion together with the cam portion.
Inner teeth are formed on the inner peripheral surface of the receiving hole, and outer teeth that engage with the inner teeth are formed on the outer peripheral surface of the pinion shaft,
A friction part for reducing a relative rotational speed of the rotating part and the cam part is formed at a contact part of the rotating part with the extending part and / or a contact part of the extending part with the rotating part. A continuously variable transmission.