JP6130223B2 - 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

  Due to the nature of such a lever crank mechanism, the load applied to the pinion shaft changes momentarily during one rotation of the turning radius adjusting mechanism (the swinging motion of the swinging link makes one reciprocation). The direction is also switched periodically.

  And since the backlash is provided between the external teeth of the pinion shaft and the internal teeth of the rotating part, when the direction of the load is switched, of the tooth surfaces of the external teeth of the pinion shaft, The tooth surface on the side that has been in contact with the internal teeth of the rotating portion is separated from the internal teeth, and the tooth surface on the opposite side that has not been in contact with the internal teeth of the rotating portion until then contacts the internal teeth.

  Therefore, at the time of switching, there is a possibility that a rattling sound is generated due to contact between the external teeth of the pinion shaft and the internal teeth of the rotating portion.

  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 reduce the rattling noise between the external teeth of the pinion shaft and the internal teeth of the rotating portion.

In order to achieve the above object, a continuously variable transmission according to the present invention includes a hollow input portion to which a driving force of a drive source is transmitted, an output shaft having a rotation center axis parallel to the rotation center axis of the input portion, and The turning radius can be adjusted and the turning radius adjustment mechanism that can rotate integrally with the input unit, the swing link supported on the output shaft, and the driving force for adjusting the turning radius are transmitted to the turning radius adjustment mechanism. A lever crank mechanism for converting the rotational movement of the turning radius adjusting mechanism into the swinging motion of the swinging link, and the swinging link on one side about the rotation center axis of the output shaft. Adjusting the radius of rotation with a one-way rotation prevention mechanism that fixes the swing link to the output shaft when trying to rotate and idles the swing link relative to the output shaft when trying to rotate to the other side The mechanism is a pin to which the driving force of the adjusting drive source is transmitted. An on-shaft, 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 pinion shaft and the cam portion are inserted at a position that is eccentric from the center; The pinion shaft is disposed inside the input unit and concentrically with the input unit, and is rotatable relative to the input unit, and has a receiving hole. Inner teeth are formed on the inner peripheral surface, outer teeth engaging with the inner teeth are formed on the outer peripheral surface of the pinion shaft, and the inner peripheral surface and the outer peripheral surface of the input unit are communicated with the peripheral surface of the input unit. A continuously variable transmission that is exposed from the notch hole and meshes with the inner tooth so that the pinion shaft moves to one side along the rotation center axis of the pinion shaft. A first urging member for urging to the other side and moving to the other side A second urging member for urging the pinion shaft, and the outer teeth of the pinion shaft and / or the inner teeth of the rotating portion are subjected to a first urging force when a load toward one side is applied to the pinion shaft. When an axial force that moves the pinion shaft in a direction opposite to the biasing direction by the member is generated and a load toward the other side is applied, the pinion shaft is in a direction opposite to the biasing direction by the second biasing member. The pinion shaft is configured as a helical gear that generates an axial force that moves the pinion shaft, an annular gear member having outer teeth formed on the outer peripheral surface, and a shaft that is inserted into the gear member and that transmits the driving force of the adjusting drive source The gear member is fitted to the shaft member so as to be movable in the axial direction, and the first biasing member and the second biasing member are disposed so as to sandwich the gear member. And it is hold | maintained at the input part by the edge part of the notch hole in the axial direction of an input part .

According to the present invention, when the direction of the load applied to the pinion shaft is switched, the impact caused by the contact between the internal teeth of the rotating part and the external teeth of the pinion shaft is moved by the helical gear in the direction of the rotation center axis. While converting into an axial force, the axial force can be absorbed by the urging member, so that rattling noise caused by an impact at the time of contact can be reduced.
In addition, when the present invention is applied to a continuously variable transmission having a plurality of lever crank mechanisms and the phases of the lever crank mechanisms being different, the direction of the axial force applied to each pinion shaft at the same time point Therefore, there is a risk that an axial load is applied to the pinion shaft.
On the other hand, in the continuously variable transmission according to the present invention, the pinion shaft is composed of a shaft member and a gear member that is movable in the axial direction with respect to the shaft member. Can be avoided.

In the continuously variable transmission of the present invention, the first biasing member and the second urging member, Oh in disc spring Rukoto are preferred.

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. FIG. 2 is a schematic diagram showing the operation of a lever crank mechanism when the amount of eccentricity is not “0” in the continuously variable transmission of FIG. 1, and (a) shows that the swing end moves from the internal dead center to the external dead center. (B) is a state in which the swing end is at the external dead center, (c) is a state in which the swing end is moving from the external dead center to the internal dead center, (d ) Shows a state in which the rocking end is at the inner dead point. 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 perspective sectional view showing a rotating disk and a pinion shaft of the continuously variable transmission of FIG. 1, (a) is a state where a load in one direction is applied to the pinion shaft, and (b) is the other side of the pinion shaft. The state where the load of the direction is added is shown. It is sectional drawing which shows the rotating disk and pinion shaft of the continuously variable transmission of FIG. 1, (a) is the state in which the load of one side direction is added with respect to the pinion shaft, (b) is the other side direction to a pinion shaft. The state where the load of is applied is shown.

  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, with reference to FIG.2 and FIG.5, the load added to the pinion shaft 7 during operation | movement of the lever crank mechanism 20 of the continuously variable transmission 1 of this embodiment is demonstrated.

  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 5 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 (a line having a length Rb) connecting the center P3 of the cam disk 5 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. 5A, 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. 5 (b), when 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. 5C, 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.

  After that, as shown in FIG. 5 (d), when the center P5 of the connecting pin 19 reaches an intermediate position between the internal dead center and the external dead center, and further starts to move toward the external dead center, The direction of the load applied to the center P3 of the rotating disk 6 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, the lever crank mechanism 20 continues to operate by sequentially repeating the states shown in FIGS. 5 (a) to 5 (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.

  Therefore, in the continuously variable transmission 1 of the present embodiment, the rotational radius adjusting mechanism 4 has a characteristic configuration and includes two urging members to reduce the occurrence of such rattling noise. Yes.

  With reference to FIGS. 2 and 6 to 8, the configuration of the turning radius adjusting mechanism 4 and the two urging members of the continuously variable transmission 1 of the present embodiment will be described in detail.

  As shown in FIG. 2, the turning radius adjusting mechanism 4 of the continuously variable transmission 1 of the present embodiment includes a pinion shaft 7 to which the driving force of the adjusting drive source 14 is transmitted and a rotation center axis P <b> 1 of the input shaft 2. A cam disk 5 that rotates integrally with the input shaft 2 in an eccentric state with respect to the input shaft 2, and a receiving hole 6 a through which the pinion shaft 7 and the cam disk 5 are inserted are provided at a position eccentric from the center. And a rotating disk 6 that is rotatable in an eccentric state.

  6 and 7, the pinion shaft 7 has an annular gear member 71 having outer teeth 7a formed on the outer peripheral surface thereof, and the driving force of the adjustment drive source 14 that is inserted through the gear member 71 is transmitted. The shaft member 72 is made up of. The gear member 71 is fitted to the shaft member 72 so as to be movable in the axial direction.

  Further, the inner teeth 6b formed on the inner peripheral surface of the receiving hole 6a of the rotating disk 6 and the outer teeth 7a formed on the outer peripheral surface of the pinion shaft 7 meshing with the inner teeth 6b are formed in a screw-like manner. It is configured as a helical gear cut into two.

  Therefore, when a load is applied from the rotary disk 6 to the pinion shaft 7 toward one side (in the state shown in FIG. 7A), the pinion shaft is moved leftward on the paper surface of FIG. When a force in the axial direction is generated to move 7 and a load toward the other side is applied (in the state shown in FIG. 7B), the pinion shaft 7 is moved to the right on the paper surface of FIG. 7B. An axial force for moving the is generated.

  Further, as shown in FIG. 8, the first disc spring 21 as the first biasing member 21 and the second biasing force are provided on the side of the gear member 71 of the pinion shaft 7 so as to sandwich the gear member 71. A second disc spring 22 as a member is disposed.

  The first disc spring 21 is configured so that when the pinion shaft 7 is rotating relative to one side with respect to the rotating disk 6 (in the state shown in FIGS. 7A and 8A), the gear of the pinion shaft 7 is used. In order to absorb the axial force generated on the member 71, the gear member 71 is opposite to the axial force (rightward on the paper surface of FIGS. 7A and 8A). Is configured to energize.

  The second disc spring 22 is a gear of the pinion shaft 7 when the pinion shaft 7 is rotating relative to the other side with respect to the rotating disk 6 (in the state of FIGS. 7B and 8B). In order to absorb the axial force generated on the member 71, the gear member 71 in a direction opposite to the axial force (leftward on the paper surface of FIGS. 7B and 8B). Is configured to energize.

  Therefore, the continuously variable transmission 1 of the present embodiment is capable of receiving an impact caused by contact between the internal teeth 6b of the rotary disk 6 and the external teeth 7a of the pinion shaft 7 when the load applied to the pinion shaft 7 is switched. The impact only increases the axial force that moves the pinion shaft 7.

  Since the increased axial force is also absorbed by the first belleville spring 21 and the second belleville spring 22 which are the two urging members, it is possible to reduce the rattling noise caused by the impact at the time of contact.

  Further, the continuously variable transmission 1 according to the present embodiment includes a plurality of lever crank mechanisms 20, and the phases of the lever crank mechanisms 20 are different from each other, so that the shaft added to each pinion shaft 7 at the same time point. The direction of the direction force is also different.

  However, since the pinion shaft 7 is composed of the shaft member 72 and the gear member 71 that is movable in the axial direction with respect to the shaft member 72, the pinion shaft 7 has a structure for reducing the rattling noise. However, no axial load is applied to the pinion shaft 7.

  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 load applied from the lever crank mechanism 20 is converted into the axial force that moves the gear member 71 of the pinion shaft 7, but the axial force that moves the rotating disk 6 instead of the pinion shaft 7. The axial force may be absorbed by an urging member such as a disc spring.

  Moreover, in the said embodiment, although the 1st disc spring 21 is used as a 1st biasing member, and the 2nd disc spring 22 is used as a 2nd biasing member, the continuously variable transmission of this invention is such a transmission. The urging member is not limited to the configuration, and may be any member that can absorb the axial force in which the load applied to the pinion shaft 7 is converted.

DESCRIPTION OF SYMBOLS 1 ... Continuously variable transmission, 2 ... Input shaft (input part), 2a ... Notch hole, 3 ... Output shaft, 4 ... Rotation radius adjustment mechanism, 5 ... Cam disk (cam part), 6 ... Rotation disk (rotation part) 6a ... receiving hole, 6b ... internal teeth, 7 ... pinion shaft, 7a ... external teeth, 71 ... gear member, 72 ... shaft member, 8 ... differential mechanism, 9 ... sun gear, 10 ... first ring gear, 11 ... first Two-ring gear, 12 ... Stepped pinion, 12a ... Large diameter portion, 12b ... Small diameter portion, 13 ... Carrier, 14 ... Adjusting drive source, 14a ... Rotating shaft, 15 ... Connecting rod, 15a ... Large diameter annular portion, 15b ... Small diameter annular portion, 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 ... connecting pin 20 lever lever mechanism, DESCRIPTION OF SYMBOLS 1 ... 1st disc spring (1st biasing member), 22 ... 2nd disc spring (2nd biasing member), i ... Transmission ratio, P1 ... Rotation center axis of the input shaft 2, P2 ... Cam disk 5 , P3, the center of the rotating disk 6, P4, the rotational center axis of the 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, R1, ... P1 and P3. Distance (eccentricity, rotational radius of the turning radius adjusting mechanism 4), R2... Distance between P4 and P5 (length of the swinging link 18), θ1... The rotation angle of the turning radius adjusting mechanism 4, .theta.2. Oscillating range.

Claims (2)

A hollow input part to which the driving force of the driving source is transmitted;
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 lever crank mechanism for converting the rotational motion of the rotational radius adjustment mechanism into the swing motion of the swing link;
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 pinion shaft to which the driving force of the adjusting drive source is transmitted, 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, A receiving hole through which the pinion shaft and the cam portion are inserted is provided at a position eccentric from the center, and has a rotating portion that is rotatable in a state of being eccentric with respect to the cam portion,
The pinion shaft is disposed inside the input unit, concentrically with the input unit, and is rotatable relative to the input unit.
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 ,
On the peripheral surface of the input portion, a notch hole that connects the inner peripheral surface and the outer peripheral surface of the input portion is formed,
The outer teeth are continuously variable transmissions that are exposed from the cutout holes and mesh with the inner teeth ,
A first urging member that urges the pinion shaft to move to one side along the rotation center axis of the pinion shaft; and a second urging member that urges the pinion shaft to move to the other side. Prepared,
The outer teeth of the pinion shaft and / or the inner teeth of the rotating portion are opposite to the urging direction by the first urging member when a load toward one side is applied to the pinion shaft. An axial direction that moves the pinion shaft in the direction opposite to the biasing direction by the second biasing member when an axial force that moves the pinion shaft in the direction is generated and a load toward the other side is applied is configured as a helical gear forces occur,
The pinion shaft is composed of an annular gear member having the outer teeth formed on the outer peripheral surface, and a shaft member that is inserted into the gear member and to which the driving force of the adjustment drive source is transmitted.
The gear member is fitted to the shaft member so as to be movable in the axial direction,
The first urging member and the second urging member are disposed so as to sandwich the gear member, and are held by the input portion at an edge portion of the notch hole in the axial direction of the input portion. A continuously variable transmission. The continuously variable transmission according to claim 1,
Wherein the first biasing member and the second urging member, a continuously variable transmission, characterized in Oh Rukoto in disc spring.