JP5836252B2 - Control device for continuously variable transmission - Google Patents

Description

  The present invention relates to a control device for a continuously variable transmission of a four-bar linkage type.

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

  The lever crank mechanism disclosed in Patent Document 1 includes a rotation radius adjustment mechanism provided on an input shaft, a swing link pivotally supported on an output shaft, and a rotation radius adjustment mechanism at one end thereof. The connecting rod has an input-side annular portion that is externally fitted and the other end portion is connected to the swing end portion of the swing link.

  The turning radius adjusting mechanism includes a disk-shaped rotating disk having a through hole formed eccentrically from the center, a ring gear provided on the inner peripheral surface of the through hole, a first fixed to the input shaft and meshed with the ring gear. One pinion, a carrier to which a driving force from an adjustment driving source is transmitted, and two second pinions that are pivotally supported by the carrier so as to rotate and revolve, and mesh with the ring gear, respectively. The first pinion and the two second pinions are arranged so that a triangle whose apex is the central axis thereof is an equilateral triangle.

  When the rotational speed of the input shaft rotated by the driving source for driving and the carrier rotated by the driving source for adjustment are the same, the eccentric amount of the center point of the rotating disk with respect to the input center axis of the input shaft is maintained and rotated. The radius of the rotation locus of the radius adjusting mechanism is also kept constant. When the rotational speed of the input shaft that is rotated by the driving source for driving and the carrier that is rotated by the driving source for adjustment are different, the eccentric amount of the center point of the rotating disk with respect to the input center axis of the input shaft changes, and the turning radius adjusting mechanism The radius of the rotation trajectory also changes.

  As the radius of the rotation locus of the rotation radius adjusting mechanism changes, the swing width of the swing end of the swing link also changes, and the gear ratio is switched to control the rotational speed of the output shaft relative to the input shaft.

  In such a continuously variable transmission, the distance between the center point of the equilateral triangle whose apex is the center axis of the three pinions and the input center axis of the input shaft, and the center point of the equilateral triangle and the center point of the rotating disk By setting the distance to be equal to each other, the input center axis and the center point of the rotating disk can be overlapped to make the amount of eccentricity zero. When the amount of eccentricity is 0, even if the input shaft is rotating, the swing width of the swing end of the swing link is 0, and the output shaft does not rotate, that is, the gear ratio is infinite. .

JP 2012-1048 A

  In a four-bar linkage type continuously variable transmission, if the speed of the output shaft decreases momentarily, as in the case of a sudden deceleration of a running vehicle, excessive torque is generated between the input shaft and the output shaft. May occur and the parts may be damaged.

  SUMMARY OF THE INVENTION In view of the above, it is an object of the present invention to provide a control device for a continuously variable transmission that can protect components without causing a clutch mechanism to function even when the rotational speed of an output shaft is greatly reduced. And

  [1] In order to achieve the above object, the present invention provides an input shaft to which a driving force from a travel drive source is transmitted, an output shaft arranged in parallel to the input shaft, and swingable to the output shaft. A plurality of lever crank mechanisms that convert a rotational movement of the input shaft into a swinging movement of the swinging link, and provided between the swinging link and the output shaft. The swing link is fixed to the output shaft when trying to rotate relative to the output shaft on one side, and the swing link relative to the output shaft when trying to rotate relative to the other side. And a one-way rotation preventing mechanism that idles, wherein the lever crank mechanism has an adjustment drive source and a rotation radius that can adjust the radius of the rotary motion on the input shaft side using the drive force of the adjustment drive source. An adjustment mechanism, and the turning radius adjustment mechanism and the swing link are coupled to each other. A control device for a continuously variable transmission including a connecting rod, wherein the turning radius adjustment mechanism includes an input element that rotates integrally with the input shaft, and an adjustment element that rotates by the adjustment drive source. The radius of rotational motion on the input shaft side is maintained when the rotational speeds of the input element and the adjustment element match, and when the rotational speeds of the input element and the adjustment element are different, An input-side rotational speed detection unit that detects the rotational speed of the input shaft, a driving force detection unit that detects the driving force of the input shaft, and a shift that detects a transmission ratio. Based on the ratio detection unit, the rotational speed detected by the input side rotational speed detection unit, the driving force detected by the driving force detection unit, and the transmission ratio detected by the transmission ratio detection unit, Drive that the adjustment drive source is transmitting to the adjustment element An adjustment driving force detection unit for calculating the maximum adjustment driving force setting unit for obtaining a maximum adjustment driving force set based on the durability of a predetermined component, and the drive detected by the adjustment driving force detection unit The driving force detected by the adjusting driving force detecting unit is set by the maximum adjusting driving force setting unit by comparing the force and the maximum adjusting driving force set by the maximum adjusting driving force setting unit. And a driving force control unit that sets the driving force output from the adjustment driving source to “0” when the driving force exceeds the maximum adjustment driving force.

  According to the present invention, when the driving force detected by the adjustment driving force detection unit exceeds the maximum adjustment driving force set by the maximum adjustment driving force setting unit by the driving force control unit, The driving force output from the driving source is set to “0”. As a result, the rotational speed of the output shaft is greatly reduced instantaneously, and the driving force detected by the adjustment driving force detection unit exceeds the maximum adjustment driving force set by the maximum adjustment driving force setting unit. Even so, the driving force output from the adjusting drive source is set to “0”, so that the adjusting element is in a freely rotating state. Therefore, even if the driving force from the travel drive source is transmitted to the input element via the input shaft, the torque of the input element is received by the idling of the adjustment element and is not transmitted to the output shaft side. Thereby, even if the rotation speed of an output shaft falls large, components can be protected.

  [2] In the present invention, the predetermined component may be a one-way rotation prevention mechanism.

Sectional drawing which shows the continuously variable transmission of embodiment of the control apparatus of this invention. Explanatory drawing which shows the turning radius adjustment mechanism, connecting rod, and rocking | fluctuation link of this embodiment from an axial direction. Explanatory drawing explaining the change of the rotation radius of the rotation radius adjustment mechanism of this embodiment. It is explanatory drawing which shows the relationship between the change of the rotation radius of the rotation radius adjustment mechanism of this embodiment, and rocking | swiveling angle (theta) ₂ of the rocking | fluctuation motion of a rocking | fluctuation link, (a) is the largest rotation radius, (b) is. (C) shows the swing angle of the swing motion of the swing link when the rotation radius is medium and the rotation radius is small. The graph which shows the change of angular velocity (omega) of a rocking | fluctuation link with respect to the change of the rotation radius of the rotation radius adjustment mechanism of this embodiment. 6 is a graph showing a state in which the output shaft is rotated by six lever crank mechanisms each having a phase difference of 60 degrees in the continuously variable transmission of the present embodiment. The block diagram which shows the structure of the control apparatus of the continuously variable transmission of this embodiment. Explanatory drawing which shows the state which the driving force transmitted from an input shaft to an output shaft increases with the rotation speed fall of an output shaft. The flowchart which shows the process of the control apparatus of this embodiment. Explanatory drawing which shows the state corresponding to FIG.8 (b) when the process of the control apparatus of this embodiment is performed.

  Hereinafter, embodiments of a control device for a four-bar linkage type continuously variable transmission according to the present invention will be described. In the four-bar linkage type continuously variable transmission of this embodiment, the speed ratio i (i = rotational speed of the input shaft / rotational speed of the output shaft) is infinite (∞), and the rotational speed of the output shaft is “0”. It is a kind of so-called IVT (Infinity Variable Transmission).

  Referring to FIGS. 1 and 2, the four-bar linkage type continuously variable transmission 1 of the present embodiment is a rotational driving force from a travel drive source 50 (see FIG. 7) such as an internal combustion engine or an electric motor. The hollow input shaft 2 that rotates about the input center axis P1 by receiving the motor, and the drive wheels 60 of the vehicle (see FIG. 7) are arranged parallel to the input shaft 2 and through a differential gear, a propeller shaft, etc., not shown. ) Includes an output shaft 3 for transmitting rotational power and six rotational radius adjusting mechanisms 4 provided on the input shaft 2.

  Each turning radius adjusting mechanism 4 includes a cam disk 5 and a rotating disk 6. 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 input center axis P1 and rotate integrally with the input shaft 2. In the present embodiment, the cam disk 5 corresponds to the input element of the present invention. Each set of cam disks 5 is arranged so as to make a round in the circumferential direction of the input shaft 2 with six sets of cam disks 5 with a phase difference of 60 degrees. In addition, a disc-shaped rotating disk 6 having a receiving hole 6a for receiving the cam disk 5 is rotatably fitted to each set of cam disks 5 in an eccentric state.

  In the rotating disk 6, the center point of the cam disk 5 is P2, the center point of the rotating disk 6 is P3, the distance Ra between the input center axis P1 and the center point P2, and the distance Rb between the center point P2 and the center point P3 are the same. So that it is eccentric with respect to the cam disk 5.

  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. The input shaft 2 is formed with a notch hole 2 a that is positioned between a pair of cam disks 5 and that communicates the inner peripheral surface and the outer peripheral surface at a location facing the eccentric direction of the cam disk 5.

  In the hollow input shaft 2, a pinion shaft 7 that is disposed concentrically with the input shaft 2 and has external teeth 7 a at locations corresponding to the rotary disk 6 is disposed so as to be rotatable relative to the input shaft 2. . The external teeth 7 a of the pinion shaft 7 mesh with the internal teeth 6 b of the rotating disk 6 through the cutout holes 2 a of the input shaft 2.

  A differential mechanism 8 is connected to the pinion shaft 7. The differential mechanism 8 is configured by 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, a sun gear 9 and A carrier 13 is provided that supports a stepped pinion 12 including a large-diameter portion 12a that meshes with the first ring gear 10 and a small-diameter portion 12b that meshes with the second ring gear 11 so as to rotate and revolve freely.

  The sun gear 9 is connected to a rotating shaft 14a of an adjustment drive source 14 composed of an electric motor for the pinion shaft 7. If the rotational speed of the adjustment 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, and the sun gear 9, the first ring gear 10, and the second ring The four elements of the 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 is. The number of rotations of the carrier 13 is (j · NR1 + Ns) / (j + 1) where j is the number of teeth of the first ring gear 10 / the number of teeth of the sun gear 9. 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 / tooth of the small diameter portion 12b) If the number)) is k, the rotation speed of the second ring gear 11 is {j (k + 1) NR1 + (k−j) Ns} / {k (j + 1)}.

  When the rotational speed of the input shaft 2 to which the cam disk 5 is fixed and the rotational speed of the pinion shaft 7 are the same, the rotating disk 6 rotates together with the cam disk 5. 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 point P <b> 2 of the cam disk 5.

  In the present embodiment, the pinion shaft 7 corresponds to the adjustment element of the present invention.

  As shown in FIG. 2, the rotating disk 6 is eccentric with respect to the cam disk 5 so that the distance Ra and the distance Rb are the same. For this reason, the center point P3 of the rotary disk 6 is positioned on the same axis as the input center axis P1, and the distance between the input center axis P1 and the center point P3, that is, the eccentricity R1 is set to “0”. it can.

  A connecting rod 15 having a large-diameter large-diameter annular portion 15a at one end and a small-diameter annular portion 15b having a smaller diameter than the large-diameter annular portion 15a at the other end is provided at the periphery of the rotating disk 6. A large-diameter annular portion 15a is rotatably fitted via a connecting rod bearing 16 made of a ball bearing. The output shaft 3 is provided with six swing links 18 corresponding to the connecting rod 15 via a one-way clutch 17 as a one-way rotation prevention mechanism.

  The one-way clutch 17 as a one-way rotation prevention mechanism is provided between the swing link 18 and the output shaft 3, and swings on the output shaft 3 when attempting to rotate relative to the output shaft 3 on one side. The link 18 is fixed, and the swing link 18 is idled with respect to the output shaft 3 when attempting to rotate relative to the other side. The swing link 18 is swingable with respect to the output shaft 3 when the one-way clutch 17 is idle with respect to the output shaft 3.

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

  FIG. 3 shows the positional relationship between the pinion shaft 7 and the rotating disk 6 in a state where the eccentricity R1 of the turning radius adjusting mechanism 4 is changed. FIG. 3A shows a state in which the amount of eccentricity R1 is “maximum”, so that the input center axis P1, the center point P2 of the cam disk 5, and the center point P3 of the rotating disk 6 are aligned. The pinion shaft 7 and the rotating disk 6 are located. At this time, 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 input center axis P1 and the center point P3 of the rotary disk 6 are located concentrically. The gear ratio i at this time is infinite (∞). The continuously variable transmission 1 of the present embodiment can adjust the radius of rotational motion on the input shaft 2 side by changing the amount of eccentricity R1 by the rotational radius adjusting mechanism 4.

  As shown in FIG. 2, the turning radius adjusting mechanism 4, the connecting rod 15, and the swing link 18 of the present embodiment 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 7 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. On the basis of this, it is repeatedly swung between the input shaft 2 and the output shaft 3 by alternately pushing to the output shaft 3 side or pulling to the input shaft 2 side.

  Since the small-diameter annular portion 15b of the connecting rod 15 is connected to the swing link 18 provided on the output shaft 3 via the 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.

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). It shows a swing range theta ₂ of the swinging link 18 for rotational movement of the rotational radius adjusting mechanism 4. As apparent from FIG. 4, as the eccentricity R1 becomes smaller, the swing range theta ₂ of the swinging link 18 is narrowed. When the eccentric amount R1 is “0”, the swing link 18 does not swing. Further, in the present embodiment, among the swing range theta ₂ of the oscillating end portion 18a of the swing link 18, the inner dead center position closest to the input shaft 2, and the outer dead center farthest position from the input shaft 2 To do.

  FIG. 5 shows the angular velocity ω accompanying the change in the eccentric amount R1 of the rotational radius adjusting mechanism 4 with the rotational angle θ of the rotational radius adjusting mechanism 4 of the continuously variable transmission 1 as the horizontal axis and the angular velocity ω of the swing link 18 as the vertical axis. The relationship of changes is shown. As can be seen from FIG. 5, the angular velocity ω of the swing link 18 increases as the eccentric amount R1 increases (the transmission ratio i decreases).

  FIG. 6 shows the rotation of the turning radius adjusting mechanism 4 when the six turning radius adjusting mechanisms 4 having different phases by 60 degrees are rotated (when the input shaft 2 and the pinion shaft 7 are rotated at the same speed). The angular velocity ω of each swing link 18 with respect to the angle θ1 is shown. As can be seen from FIG. 6, the output shaft 3 is smoothly rotated by the six lever crank mechanisms 20.

  FIG. 7 shows a block diagram of a control device 40 that controls the continuously variable transmission 1 of the present embodiment. The control device 40 is an electronic unit composed of a CPU, a memory, and the like, and fulfills the function of controlling the amount of eccentricity of the turning radius adjusting mechanism 4 by executing a control program held in the memory by the CPU.

  Further, the control device 40 has a limit value (maximum value) that can prevent a decrease in durability of the one-way clutch 17 in relation to the driving force (torque) of the input shaft 2, the gear ratio, and the rotational speed of the output shaft 3. The driving force (maximum torque) of the adjusting drive source 14 is obtained in advance through experiments or the like, and the obtained maximum torque is related to the driving force (torque) of the input shaft 2, the gear ratio, and the rotational speed of the output shaft 3. A storage unit 40a is provided for storing the information as table or map information.

  The travel drive source 50 includes an input side rotational speed detection unit 52 that detects the rotational speed of the travel drive source 50, and a drive force detection unit 54 that detects a drive force (torque) output from the travel drive source 50. Is provided. The control device 40 can receive information on the input side rotational speed of the traveling drive source 50 detected by the input side rotational speed detection unit 52, and the traveling drive source 50 detected by the driving force detection unit 54 outputs the information. The driving force (torque) information to be received can be received.

  Further, the continuously variable transmission 1 is provided with an output side rotational speed detection unit 56 that detects the rotational speed of the output shaft 3. The control device 40 is configured to be able to receive information on the output side rotational speed obtained by detecting the rotational speed of the output shaft 3 detected by the output side rotational speed detection unit 56.

  The control device 40 is provided with a processing unit 40b that calculates a gear ratio from the received input side rotational speed and output side rotational speed. That is, the processing unit 40b of the present embodiment also functions as a gear ratio detection unit that detects the gear ratio of the present invention. The control device 40 is configured to receive predetermined vehicle information such as the vehicle speed and the accelerator opening, and the processing unit 40b sets a target gear ratio based on the predetermined vehicle information, and the continuously variable transmission. A program for controlling the operation of the adjustment drive source 14 so that the gear ratio of 1 becomes the target gear ratio is also stored.

  FIG. 8 shows the relationship between the angular velocity of the oscillating end 18a of one oscillating link 18 and the rotational velocity of the output shaft 3, where the horizontal axis is time (or the rotational angle of the input shaft 2) and the vertical axis is the angular velocity. Is shown. As shown by hatching in FIG. 8A, a region where the angular velocity of the oscillating end 18 a exceeds the rotational speed of the output shaft 3, and after the angular velocity of the oscillating end 18 a falls below the rotational speed of the output shaft 3. A driving force is transmitted from the input shaft 2 to the output shaft 3 via the lever crank mechanism 20 until the twist (several degrees of twist) of the one-way clutch 17 is released.

  Here, as shown in FIG. 8B by hatching different from that in FIG. 8A, when the rotational speed of the output shaft 3 significantly decreases instantaneously, such as when the vehicle suddenly decelerates, the input shaft 2 to the output shaft The driving force transmitted to 3 increases rapidly. When the driving force transmitted from the input shaft 2 to the output shaft 3 increases rapidly, an excessive force is applied to the one-way clutch 17 and the output shaft 3, and there is a risk that durability and life will be reduced.

  Therefore, in the control device 40 of the continuously variable transmission 1 according to the present embodiment, the one-way clutch 17 is executed even if the rotation speed of the output shaft 3 rapidly decreases by executing the processing shown in FIG. 9 with a predetermined cycle time. It is possible to prevent a decrease in durability.

  The process shown in FIG. 9 will be described in detail below. First, the processing unit 40b of the control device 40 receives the input side rotational speed detected by the input side rotational speed detection unit 52 and the input side driving force detected by the driving force detection unit 54 in Step 1 of FIG. Then, the driving force (torque) Tp that the adjustment drive source 14 needs to output in order to maintain the current gear ratio is obtained from the gear ratio obtained by the processing unit 40b. The table or map data required at this time is also stored in advance in the storage unit 40a. That is, the processing unit 40b of the present embodiment also has the function of the adjustment driving force detection unit of the present invention, and the processing of step 1 corresponds to the processing of the adjustment driving force detection unit of the present invention.

  Further, based on the output side rotational speed detected by the output side rotational speed detection unit 56, the maximum torque Tmax is obtained from the data stored in the storage unit 40a. That is, the processing unit 40b of the present embodiment also has the function of the maximum adjustment driving force setting unit of the present invention, and the processing of Step 1 corresponds to the processing of the maximum adjustment driving force setting unit of the present invention.

  Next, the process proceeds to step 2, and it is determined whether or not the current driving force Tp is equal to or less than the maximum torque Tmax. If the current driving force Tp is equal to or less than the maximum torque Tmax (in the case of “Yes” in STEP 2 in FIG. 9), the current process is terminated. When the current driving force Tp exceeds the maximum torque Tmax (in the case of “No” in STEP 2 of FIG. 9), the process proceeds to Step 3, and the control device 40 drives the driving force Tp (output torque) of the adjusting drive source 14. Zero torque control is executed with “0”.

  That is, the processing unit 40b of this embodiment also has a function as the driving force control unit of the present invention, and Steps 2 and 3 correspond to the processing of the driving force control unit of the present invention.

  According to the control device 40 of the present embodiment, when the driving force Tp of the adjusting drive source 14 exceeds the maximum torque Tmax as the maximum adjusting driving force in step 2 of FIG. 9, step 3 of FIG. Thus, zero torque control is performed with the driving force output from the adjustment driving source 14 as “0”.

  As a result, even if the rotational speed of the output shaft 3 is greatly reduced momentarily and the driving force Tp of the adjusting drive source 14 exceeds the maximum torque Tmax as the maximum adjusting drive force, the adjusting drive Since the driving force output from the source 14 is set to “0”, the pinion shaft 7 as the adjusting element is in a state of free rotation.

  Therefore, even if the driving force from the traveling drive source 50 is transmitted to the cam disk 5 as the input element via the input shaft 2, the torque of the cam disk 5 as the input element is the same as that of the pinion shaft 7 as the adjustment element. It is swept away by idling and is not transmitted to the output shaft 3 side.

  As a result, as shown in FIG. 10, even if there is a possibility that the rotational speed of the output shaft 3 is drastically reduced and the durability of the one-way clutch 17 is likely to be reduced, The eccentric amount R1 of the radius adjusting mechanism 4 can be quickly reduced, the one-way clutch 17 can be protected, and the durability of the one-way clutch 17 can be prevented from being lowered.

  In the present embodiment, the one that prevents a decrease in the durability of the one-way clutch 17 has been described. However, the control device of the present invention is not limited to this. For example, the durability of the output shaft 3 may be prevented from being lowered. In this case, the storage unit 40a has a limit value (maximum value) that can prevent a decrease in durability of the output shaft 3 in relation to the driving force (torque) of the input shaft 2, the transmission ratio, and the rotational speed of the output shaft 3. A state in which the driving force (maximum torque) of the adjusting drive source 14 is obtained in advance through experiments or the like, and the obtained maximum torque is related to the driving force (torque) of the input shaft 2, the gear ratio, and the rotational speed of the output shaft 3. The information may be stored as table or map information.

  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. May be configured by a two-way clutch (two-way clutch) configured to be able to switch the rotation direction of the swing link 18 capable of transmitting the rotation with respect to the output shaft 3.

  Moreover, in this embodiment, although the thing provided with the cam disk 5 and the rotation disk 6 which rotate integrally with the input shaft 2 as the rotation radius adjustment mechanism 4 was demonstrated, the rotation radius adjustment mechanism 4 of this invention is the following. Not limited to this. For example, the turning radius adjustment mechanism is a disc-shaped rotating disk having a through hole formed eccentrically from the center, a ring gear provided on the inner peripheral surface of the through hole, and fixed to the input shaft and meshed with the ring gear. And a carrier to which the driving force from the adjusting drive source is transmitted, and two second pinions that are pivotally supported by the carrier so as to rotate and revolve, and mesh with the ring gear, respectively. Also good. In this case, the input element is the first pinion and the adjustment element is the carrier.

DESCRIPTION OF SYMBOLS 1 Continuously variable transmission 2 Input shaft 2a Notch hole 3 Output shaft 4 Turning radius adjustment mechanism 5 Cam disk (input element)
6 Rotating disc 6a Receiving hole 6b Internal tooth 7 Pinion shaft (adjustment element)
7a External teeth 8 Differential mechanism (planetary gear mechanism)
8a Differential mechanism case 9 Sun gear 10 First ring gear 11 Second ring gear 12 Stepped pinion 12a Large diameter portion 12b Small diameter portion 13 Carrier 14 Adjustment drive source (motor)
14a Rotating shaft 15 Connecting rod 15a Large-diameter annular portion 15b Small-diameter annular portion 15c Lubricating oil hole 16 Connecting rod bearing 17 One-way clutch (one-way rotation prevention mechanism)
18 swing link 18a swing end 18b protrusion 18c through hole 19 connecting pin 20 lever crank mechanism (four-bar link mechanism)
21 Oil passage pipe 21a Discharge hole 22 Boundary plane 30 Transmission case 40 Controller 40a Storage unit 40b Processing unit (speed ratio detection unit, adjustment driving force detection unit, maximum adjustment driving force setting unit, driving force control unit)
50 Traveling drive source 52 Input side rotational speed detection unit 54 Driving force detection unit 56 Output side rotational speed detection unit 60 Driving wheel P1 Input center axis P2 Center point P3 of the cam disk Distance Rb between the center points Ra P1 and P2 of the rotating disk Distance R1 between P2 and P3 Eccentricity (distance between P1 and P3)
rotation angle theta ₂ swing range of θ1 rotational radius adjusting mechanism.

Claims (2)

An input shaft to which driving force from the driving source for traveling is transmitted;
An output shaft disposed parallel to the input shaft;
A plurality of lever crank mechanisms that have a swing link that is pivotally supported by the output shaft, and that converts a rotational motion of the input shaft into a swing motion of the swing link;
The swing link is provided between the swing link and the output shaft, and the swing link is fixed to the output shaft when attempting to rotate relative to the output shaft and relatively rotated toward the other side. A one-way rotation prevention mechanism that idles the swing link with respect to the output shaft when
The lever crank mechanism includes an adjustment drive source, a rotation radius adjustment mechanism capable of adjusting a radius of rotational motion on the input shaft side using a drive force of the adjustment drive source, the rotation radius adjustment mechanism, and the swinging mechanism. A control device for a continuously variable transmission comprising a connecting rod for connecting a dynamic link,
The turning radius adjustment mechanism includes an input element that rotates integrally with the input shaft, and an adjustment element that is rotated by the adjustment drive source, and when the rotational speeds of the input element and the adjustment element coincide with each other, The radius of the rotational motion on the input shaft side is maintained, and the radius of the rotational motion on the input shaft side is changed when the rotational speeds of the input element and the adjustment element are different,
An input side rotational speed detection unit for detecting the rotational speed of the input shaft;
A driving force detector for detecting the driving force of the input shaft;
A transmission ratio detection unit for detecting the transmission ratio;
Based on the rotational speed detected by the input-side rotational speed detection unit, the driving force detected by the driving force detection unit, and the speed ratio detected by the speed ratio detection unit, the adjustment drive source is An adjustment driving force detector for calculating the driving force transmitted to the adjustment element;
A maximum adjustment driving force setting unit for obtaining a maximum adjustment driving force set based on the durability of a predetermined part;
The driving force detected by the adjusting driving force detecting unit by comparing the driving force detected by the adjusting driving force detecting unit with the maximum adjusting driving force set by the maximum adjusting driving force setting unit. A driving force control unit that sets the driving force output from the adjustment driving source to “0” when the driving force exceeds the maximum adjusting driving force set by the maximum adjusting driving force setting unit. A control device for a continuously variable transmission. A control device for a continuously variable transmission according to claim 1,
The control device for a continuously variable transmission, wherein the predetermined component is the one-way rotation prevention mechanism.

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