JP6097727B2 - Continuously variable transmission - Google Patents

Description

  The present invention relates to a crank type continuously variable transmission.

  Patent Document 1 discloses a plurality of crank-type transmission units that convert rotation of an input shaft connected to an engine into reciprocating motion of a connecting rod, and convert reciprocating motion of the connecting rod into rotational motion of an output shaft by a one-way clutch. A continuously variable transmission provided and a control device for the continuously variable transmission are disclosed.

  Each transmission unit of the continuously variable transmission disclosed in Patent Document 1 includes a fixed disk that is eccentrically provided on an input shaft, and a swinging disk that is eccentrically provided on the fixed disk and is rotatably provided. A one-way clutch is provided between the swing link and the output shaft. The one-way clutch fixes the swing link to the output shaft when the swing link is about to rotate relative to the output shaft, and To idle the swing link.

  A pinion shaft is inserted into the input shaft, and a notch hole is formed at a location facing the eccentric direction of the fixed disk, and the pinion shaft is exposed from the notch hole. The swing disk is provided with a receiving hole for receiving the input shaft and the fixed disk. Inner teeth are formed on the inner peripheral surface of the swing disk that forms the receiving hole. The inner teeth mesh with the pinion shaft exposed from the notch hole of the input shaft. When the input shaft and the pinion shaft are rotated at the same speed, the eccentric amount of the eccentric mechanism in the transmission unit is maintained. When the rotational speeds of the input shaft and the pinion shaft are made different, the amount of eccentricity of the eccentric mechanism in the transmission unit is changed, and the gear ratio changes.

  When the eccentric mechanism of the transmission unit is rotated by rotating the input shaft, the large-diameter annular portion of the connecting rod rotates, and the swing end of the swing link connected to the other end of the connecting rod Swing. Since the swing link is provided on the output shaft via the one-way clutch, the rotational drive force (torque) is transmitted to the output shaft only when rotating to one side.

  In the continuously variable transmission described above, the amount of eccentricity of the eccentric mechanism in the transmission unit is changed according to the phase of the rotating shaft of the electric motor that rotationally drives the pinion shaft. In order to estimate the amount of eccentricity of the eccentric mechanism, the control device disclosed in Patent Document 1 rotates an input shaft that generates a predetermined number of pulses (input shaft rotation reference pulse number Ki) each time the input shaft rotates once. An angle sensor and a motor rotation angle sensor that generates a predetermined number of pulses (motor rotation reference pulse number Km) each time the rotation shaft of the motor rotates once are used. The control device includes a cumulative input shaft rotation number Mi (= Pi / Ki) calculated based on a cumulative input shaft pulse Pi that is a cumulative value of pulses output from the input shaft rotation angle sensor after the engine is started. From the accumulated motor rotation number Mm (= Pm / Km) calculated based on the accumulated motor pulse Pm, which is the accumulated value of the pulses output from the motor rotation angle sensor after the engine is started, the eccentricity estimation function h ( The amount of eccentricity of the eccentric mechanism is estimated by Mi, Mm).

  Furthermore, the control device performs various controls related to the operation of the continuously variable transmission after deriving each torque (input / output torque) transmitted to the input shaft and the output shaft based on the estimated value of the eccentricity. For derivation of the input torque based on the estimated value of the eccentricity, a table corresponding to the relationship between the eccentricity R1, the gear ratio i, and the input torque Ti as shown in FIG. 17 is used. Similarly to the input torque Ti, a table corresponding to the relationship between the eccentricity R1, the gear ratio i, and the output torque To is used for the output torque To. These tables are determined in advance by experiments or the like and stored in a memory or the like.

JP 2012-251608 A

  The control device for a continuously variable transmission described in Patent Document 1 described above uses a pulse generated by the input shaft rotation angle sensor and a pulse generated by the motor rotation angle sensor when estimating the amount of eccentricity of the eccentric mechanism. Yes. The pulse generated by the input shaft rotation angle sensor is in accordance with the rotation of the input shaft, but the input shaft may sometimes change over time due to wear or the like. The pulse generated by the electric motor rotation angle sensor corresponds to the rotation of the electric motor that rotationally drives the pinion shaft, and the electric motor rotation angle sensor can also be said to generate a pulse corresponding to the rotation of the pinion shaft. The pinion shaft meshes with the internal teeth formed on the inner peripheral surface of the swing disk, and a gap called “backlash” is provided between the pinion shaft and the internal teeth. If the error included in the pulse generated by each sensor increases due to such aging or backlash, the accuracy of the estimated amount of eccentricity decreases.

  Since the control device for the continuously variable transmission derives the input / output torque based on the estimated value of the eccentricity, it is desirable that the error included in the pulse generated by each sensor is small. For this reason, with respect to the aging described above, it is possible to reduce the error to some extent by taking measures such as forming a rotating member using a highly wear-resistant material or performing periodic maintenance. Further, for the backlash described above, a certain degree of error reduction can be realized by setting at the time of assembly. However, if such measures are not taken, the error included in the pulse generated by each sensor becomes large, and the accuracy of the estimated value of the eccentricity is reduced. In addition, the accuracy of the input / output torque derived by the control device based on the estimated value of the eccentricity amount also decreases.

  An object of the present invention is to provide a continuously variable transmission capable of deriving a highly accurate eccentric amount.

In order to achieve the above object, the invention described in claim 1
An input shaft (for example, an input shaft 2 in an embodiment described later) to which a driving force (for example, an internal combustion engine E in an embodiment described later) is transmitted;
An output shaft (for example, an output shaft 3 in an embodiment described later) disposed in parallel with the input shaft;
A rotation radius adjustment mechanism (for example, a rotation radius adjustment mechanism 4 in an embodiment described later) that is rotatable about the input shaft and that can adjust a rotation radius (for example, an eccentricity R1 in the embodiment described later); A plurality of oscillating links (for example, oscillating links 18 in the embodiments described later) supported by the output shaft, and a plurality of components that convert the rotational motion of the input shaft into the oscillating motion of the oscillating links. A lever crank mechanism (for example, a lever crank mechanism 20 in an embodiment described later);
The swing link is fixed to the output shaft when the swing link is about to rotate to one side around the output shaft, and the swing shaft is fixed to the output shaft when the swing link is about to rotate to the other side. A continuously variable transmission (for example, a continuously variable transmission 1 in an embodiment described later) including a one-way rotation prevention mechanism (for example, a one-way clutch 17 in an embodiment described later) that idles the swing link. And
A protruding portion (for example, a protruding portion 28 in an embodiment described later) inclined in the circumferential direction is provided on a part of the outer periphery of the swing link,
A plurality of detection units (for example, gap sensors 35A and 35B in the embodiments described later) are provided on the outer peripheral side of the swing link and detect the distance to the outer peripheral surface of the swing link including the raised portion. ,
The difference between the values detected by any two of the plurality of detectors continuously changes according to the swing motion of the swing link.

The invention according to claim 2 is the invention according to claim 1,
The difference value between the values detected by each of the two arbitrary detection units is centered on the difference value when the swing angle of the swing link is a half value of the maximum angle according to the swing motion of the swing link. Increase or decrease symmetrically.

In the invention according to claim 3, in the invention according to claim 2,
The sum of the values detected by the two arbitrary detectors is constant regardless of the swing motion of the swing link.

The invention according to claim 4 is the invention according to any one of claims 1 to 3,
The plurality of detectors are arranged at positions where the lever crank mechanism does not straddle a load direction applied to the output shaft via the swing link.

The invention according to claim 5 is the invention according to any one of claims 1 to 4,
The output shaft is supported by a bearing z;
The detection unit is disposed on the outer peripheral side of the swing link close to the bearing.

The invention according to claim 6 is the invention according to any one of claims 1 to 5,
The plurality of detection units are arranged at different positions along the circumferential direction of the swing link with respect to the raised portions provided on the outer periphery of the swing link.

The invention according to claim 7 is the invention according to any one of claims 1 to 5,
The raised portion has a plurality of raised portions having different phases with respect to the circumferential direction of the swing link, and the plurality of raised portions are each in the axial direction of the output shaft (for example, rotation in an embodiment described later). Arranged at different positions on the central axis P4),
Each of the plurality of detection units is arranged in the axial direction corresponding to each of the plurality of raised portions, and is arranged at the same position in the circumferential direction of the swing link.

The invention according to claim 8 is the invention according to any one of claims 1 to 7,
The two arbitrary detectors are configured with respect to a surface formed on a rotation center axis of the output shaft in a direction perpendicular to a load direction applied by the lever crank mechanism to the output shaft via the swing link. The oscillating link is disposed at a symmetrical position in the circumferential direction.

  According to the first aspect of the present invention, the turning radius (the amount of eccentricity) of the turning radius adjusting mechanism is estimated based on a difference between detected values that continuously change according to the swinging motion of the swinging link. The plurality of detectors detect the distance to the outer peripheral surface of the swing link including the raised portion, and do not detect the rotation state of the rotating member such as the rotation speed and the rotation angle. Therefore, the error due to the secular change of the rotating member, backlash, etc. in the detection values of the plurality of detection units is very small. As described above, since the detection values obtained from the plurality of detection units are highly accurate, it is possible to derive a highly accurate turning radius (an eccentric amount).

  According to the invention of claim 2, according to the swinging motion of the swing link, the difference value of each detected value is symmetrical with respect to the difference value when the swing angle of the swing link is a half value of the maximum angle. Therefore, the swing range of the swing link can be estimated. Since the error included in the detection value is small and the accuracy of the estimated value of the swing range is high, the amount of eccentricity corresponding to the swing range can be derived with high accuracy.

  According to the invention of claim 3, since the half value of the sum of the detected values is constant, the amount of expansion of the swing link can be derived based on the half value of the sum of the detected values. Since the error included in the detection value is small and the detection values of the plurality of detection units are values near the output shaft, a more accurate output torque can be derived.

  According to the fourth aspect of the present invention, since the plurality of detection units are installed at positions away from the load direction, the detection value is not affected as much as possible by the distortion or the like that the output shaft receives.

  According to the fifth aspect of the present invention, the detection values of the plurality of detection units set at a place where the influence of the distortion or the like received by the output shaft is suppressed by the bearing are not affected by the influence of the distortion or the like as much as possible.

  According to the invention of claim 6, a single raised portion may be provided on a part of the outer periphery of the swing link.

  According to invention of Claim 7, the relationship between the shape of each protruding part and the position of a detection part can be set for every detection value. Moreover, since a some detection part is arrange | positioned in the same position in the circumferential direction, a detection value receives to the influence of the same pipe expansion.

  According to the eighth aspect of the present invention, since the plurality of detection units are installed at positions away from the load direction, the detected value is least affected by the distortion or the like that the output shaft receives.

It is a block diagram which shows the internal structure of the vehicle containing the continuously variable transmission of this embodiment. It is sectional drawing of the axial direction which shows embodiment of the continuously variable transmission of this invention. It is a schematic diagram which shows the turning radius adjustment mechanism, connecting rod, and rocking | fluctuation link of the continuously variable transmission shown in FIG. 2 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. FIG. 3 is a schematic diagram showing the relationship between the change in the rotation radius of the rotation radius adjustment mechanism of the continuously variable transmission of FIG. 2 and the swing angle of the swing motion of the swing link, where (a) shows the maximum rotation radius; ) Shows the case where the turning radius is medium, and (c) shows the case where the turning radius is small. It is a graph which shows the change of the angular velocity of the rocking | fluctuation link with respect to the change of the rotation radius of the rotation radius adjustment mechanism of the continuously variable transmission of FIG. 3 is a graph showing a state where an output shaft is rotated by a lever crank mechanism of the continuously variable transmission of FIG. 2. FIG. 3 is a schematic diagram showing a relationship between cam disks of a lever crank mechanism of the continuously variable transmission shown in FIG. 2, (a) is an arrangement relationship of each cam disk, (b) is a phase relationship of each cam disk, ( c) shows the inter-axis distance relationship of each cam disk. It is a figure which shows the positional relationship of the protruding part provided in the cyclic | annular part of the rocking | fluctuation link, and a sensor when it sees from an axial direction. It is a graph which shows an example of the detected value of two sensors obtained when rocking motion is performed to the maximum in the continuously variable transmission when pipe expansion does not occur, and a value related to the detected value. It is a graph which shows an example of the detected value of two sensors obtained when rocking motion is performed to the maximum in the continuously variable transmission in the case where pipe expansion occurs, and a value related to the detected value. It is sectional drawing of the axial direction of the continuously variable transmission which concerns on a modification. It is a graph which shows the other example of the detected value of two sensors obtained when rocking motion is performed to the maximum in the continuously variable transmission when pipe expansion does not occur, and the value related to the detected value. It is a figure which shows the positional relationship of the protruding part provided in the cyclic | annular part of the rocking | fluctuation link corresponding to FIG. 13, and two sensors when it sees from an axial direction. It is a figure which shows the form by which two protruding parts arrange | positioned in the position where a phase differs with respect to the circumferential direction were provided along with the axial direction, and two sensors were arranged along with the axial direction at the same circumferential direction position. It is a graph which shows the value relevant to the other example of the detected value of two sensors obtained when a rocking | fluctuation motion is performed to the maximum in a continuously variable transmission, and the said detected value. It is a figure which shows the relationship between eccentricity, a gear ratio, and input torque.

  Hereinafter, embodiments of the continuously variable transmission of the present invention will be described.

  FIG. 1 is a block diagram showing an internal configuration of a vehicle including a continuously variable transmission according to this embodiment. A continuously variable transmission 1 mounted on the vehicle shown in FIG. 1 transmits driving force from a driving source such as an internal combustion engine E to driving wheels W and W via left and right axles. The vehicle includes a management ECU 50 that controls the gear ratio of the continuously variable transmission 1.

  The continuously variable transmission 1 according to the present embodiment is a four-bar linkage type continuously variable transmission, and the transmission ratio i (i = rotational speed of the input shaft / rotational speed of the output shaft) is set to infinity (∞). It is a kind of transmission that can make the rotation speed of the output shaft “0”, so-called IVT (Infinity Variable Transmission).

  First, with reference to FIG.2 and FIG.3, the structure of the continuously variable transmission 1 of this embodiment is demonstrated.

  The continuously variable transmission 1 according to the present embodiment includes an input shaft 2, an output shaft 3, an input shaft rotational speed sensor 31, an output shaft rotational speed sensor 33, and six rotational radius adjusting mechanisms 4. The continuously variable transmission 1 is housed in a transmission case 21. The transmission case 21 has one end wall portion 21a, the other end wall portion 21b disposed opposite to the one end wall portion 21a and fixed to the engine ENG, the outer edge of the one end wall portion 21a, and the other end wall portion 21b. It is formed by the peripheral wall part 21c which connects an outer edge. The one end wall 21a and the other end wall 21b are formed with an input shaft side opening for supporting the input shaft 2 and an output shaft side opening for supporting the output shaft 3, respectively. An input shaft bearing 22 and an output shaft bearing 23 are fitted into the input shaft side opening and the output shaft side opening.

  The input shaft 2 is a hollow member, and rotates around the rotation center axis P1 of the input shaft 2 by receiving a rotational driving force from a driving source such as the internal combustion engine E 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 W of the vehicle via a differential gear D, an axle, or the like.

  The input shaft rotational speed sensor 31 detects the rotational speed Nin per unit time of the input shaft 2 of the continuously variable transmission T. A signal indicating the rotational speed Nin of the input shaft 2 detected by the input shaft rotational speed sensor 31 is sent to the management ECU 33.

  The output shaft rotational speed sensor 33 detects the rotational speed Nout per unit time of the output shaft 3 of the continuously variable transmission T. A signal indicating the rotational speed Nout of the output shaft 3 detected by the output shaft rotational speed sensor 33 is sent to the management ECU 33.

  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 arranged so as to make a round in the circumferential direction of the input shaft 2 with six sets of cam disks 5.

  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. External teeth 7 a provided on the outer periphery of the pinion shaft 7 mesh with internal teeth 6 b provided on the inner periphery of the receiving hole 6 a of the rotary disk 6. Further, a differential mechanism 8 is connected to the pinion shaft 7.

  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)}.

  Therefore, 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 input shaft 2 to which the cam disk 5 is fixed and the rotational speed of the pinion shaft 7 are the same. In some cases, the rotating disk 6 rotates together with the cam disk 5. On the other hand, when there is a difference between the rotation speed of the input shaft 2 and the rotation speed of the pinion shaft 7, the rotating disk 6 rotates around the center P <b> 2 of the cam disk 5.

  As shown in FIG. 3, 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 concentrically with 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 amount of eccentricity R1 is expressed as “ 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. When the swing link 18 is fixed to the output shaft 3 by the one-way clutch 17 and torque is transmitted to the output shaft 3, the swing link 18 is pushed from the inner diameter side by the one-way clutch 17 and the outer diameter thereof is increased. Increases slightly. Hereinafter, the slight increase in the outer diameter of the swing link 18 at this time is referred to as “tube expansion”. Further, the amount of increase in the outer diameter of the swing link 18 at the time of tube expansion is referred to as “tube expansion amount”.

  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. Further, the swing link 18 is provided with an annular portion 18d. A protruding portion 28 that is inclined in the circumferential direction of the swing link 18 is provided on a part of the annular portion 18d on the side away from the swing end portion 18a across the rotation center axis P4. The raised portion 28 continuously protrudes from the annular portion 18d in a direction in which the outer peripheral surface is separated from the output shaft 3, and forms a part of the outer peripheral surface of the annular portion 18d.

  In the present embodiment, the one-way clutch 17 is used as the one-way rotation prevention mechanism, but the one-way rotation prevention mechanism used in the continuously variable transmission of the present invention is not limited to this, and is output from the swing link 18. You may comprise with the two-way clutch (two-way clutch) comprised so that the rotation direction with respect to the output shaft 3 of the rocking | fluctuation link 18 which can transmit a torque to the axis | shaft 3 is changeable.

  Next, the lever crank mechanism of the continuously variable transmission 1 according to the present embodiment will be described with reference to FIGS.

  As shown in FIG. 3, in the continuously variable transmission 1 according to the present embodiment, the turning radius adjusting mechanism 4, the connecting rod 15, and the swing link 18 constitute a lever crank mechanism 20 (four-bar linkage mechanism). 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. 2, 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. 4, the rotation radius of the rotation radius adjustment mechanism 4, that is, the eccentric amount R1 is adjustable.

  FIG. 4A shows a state in which the eccentric amount R1 is set to “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. 4B shows a state where the eccentric amount R1 is set to “medium” which is smaller than that in FIG. 4A, and FIG. 4C shows 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. 4A in FIG. 4B, and “large” which is larger than the gear ratio i in FIG. 4B in FIG. Become. FIG. 4D shows a state where the 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. 5 is a schematic diagram showing the relationship between the rotation radius of the rotation radius adjusting mechanism 4 of this embodiment, that is, the change in the eccentricity R1 and the swing angle (swing range) of the swinging motion of the swing link 18. FIG.

  FIG. 5A shows the case where the eccentric amount R1 is “maximum” in FIG. 4A (when the gear ratio i is the minimum), and FIG. 5B shows the amount of eccentricity R1 in FIG. FIG. 5C shows the case where the eccentric amount R1 is “small” in FIG. 4C (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. 5, 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.

  6 shows the angular velocity associated with the change in the eccentric amount R1 of the rotating radius adjusting mechanism 4 with the phase θ1 of the rotating 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. It is a figure which shows the relationship of the change of (omega).

  As can be seen from FIG. 6, the angular velocity ω of the swing link 18 increases as the eccentric amount R1 increases (the transmission ratio i decreases).

  Further, FIG. 7 shows each oscillation with respect to the phase θ1 of the rotation radius adjustment mechanism 4 when the six rotation radius adjustment mechanisms 4 are rotated (when the input shaft 2 and the pinion shaft 7 are rotated at the same speed). It is a figure which shows angular velocity (omega) of the link.

  It can be seen from FIG. 7 that the output shaft 3 is smoothly rotated by the six lever crank mechanisms 20.

  Further, as shown in FIG. 2, the continuously variable transmission 1 of the present embodiment includes six lever crank mechanisms 20.

  In the continuously variable transmission 1 of the present embodiment, as shown in FIG. 8 (a), the turning radius adjusting mechanism 4 of each of the six lever crank mechanisms 20 is provided on the side opposite to the engine. That is, in order from the adjustment drive source (ACT) 14 side, the first to sixth turning radius adjustment mechanisms 4a to 4f are used, and each set of cam disks 5 included in each of them is referred to as the first to sixth cam disks 5a. ~ 5f. Further, the swing links 18 included in each of the six lever crank mechanisms 20 are first to sixth swing links 18A to 18F in order from the adjustment drive source 14 side.

  And as shown in FIG.8 (b), the phase of the 1st cam disk 5a and the 2nd cam disk 5b has shifted | deviated 180 degrees. Further, the phases of the second cam disk 5b and the third cam disk 5c are shifted by 60 ° counterclockwise in FIG. 8B. The phases of the third cam disk 5c and the fourth cam disk 5d are shifted by 180 °. The phases of the fourth cam disk 5d and the fifth cam disk 5e are shifted by 60 ° counterclockwise in FIG. 8B. The phases of the fifth cam disk 5e and the sixth cam disk 5f are shifted by 180 °.

  Further, as shown in FIG. 8C, the cam disks 5 a to 5 f are arranged at equal intervals in the axial direction of the input shaft 2.

  In the continuously variable transmission 1 according to the present embodiment, the phase of the first to sixth cam disks 5a to 5f, that is, the phase and arrangement of the first to sixth turning radius adjusting mechanisms 4a to 4f are set in such a relationship. Accordingly, the centrifugal forces generated in the respective turning radius adjusting mechanisms 4 cancel each other, and vibrations generated when the respective turning radius adjusting mechanisms 4 rotate are suppressed.

  In order to estimate the eccentric amount R1 in the continuously variable transmission 1 described above, in this embodiment, the swing range θ2 of the swing link 18 shown in FIG. 5 is detected. The relationship between the swing range θ2 of the swing link 18 and the eccentric amount R1 is as shown in FIG. The eccentric amount R1 is larger as the swing range θ2 is larger. Therefore, the eccentric amount R1 corresponding to the swing range θ2 of the swing link 18 is derived from a specific relationship in the four-bar linkage mechanism of the continuously variable transmission 1.

  As shown in FIG. 9, the continuously variable transmission 1 includes two gap sensors 35A and 35B in order to detect the swing range θ2. Gap sensors (hereinafter simply referred to as “sensors”) 35 </ b> A and 35 </ b> B detect the distance to the outer peripheral surface of the swing link 18 including the raised portion 28 in a non-contact manner. The sensors 35 </ b> A and 35 </ b> B are arranged at different positions with respect to the raised portion 28 along the circumferential direction of the swing link 18. In the example shown in FIG. 9, the output shaft in a direction perpendicular to the direction in which the output shaft 3 receives a load (load direction) when the rotational motion of the turning radius adjusting mechanism 4 is converted into the swing motion of the swing link 18. Sensors 35A and 35B are arranged at positions symmetrical in the circumferential direction of the swing link 18 with respect to the plane p formed on the center line 3 of FIG. However, the sensors 35A and 35B are disposed at positions that satisfy the condition that the angle in the circumferential direction from the virtual line indicating the load direction to the sensor 35A or the sensor 35B satisfies 45 degrees or more. Thus, the sensors 35A and 35B are equally arranged at positions that do not cross the load direction and are away from the imaginary line indicating the load direction. As a result, the detection values of the sensors 35A and 35B are not affected as much as possible by the distortion or the like that the output shaft 3 receives.

  Further, the sensor 35A is disposed at a position for detecting the distance to the thinnest outer peripheral surface of the raised portion 28 in a state where the swing link 18 is not swinging. On the other hand, the sensor 35B is disposed at a position for detecting the distance to the thickest outer peripheral surface of the raised portion 28 in a state where the swing link 18 is not swinging. The relationship between the separation angle α in the circumferential direction of the two sensors 35A and 35B and the separation angle β in the circumferential direction of the one-way clutch 17 provided on the inner diameter side of the swing link 18 is expressed as α ≠ nβ (n Is a positive integer). Further, the continuously variable transmission 1 of the present embodiment includes six lever crank mechanisms 20, but the sensors 35 </ b> A and 35 </ b> B are levers adjacent to the input shaft bearing 22 and the output shaft bearing 23 that are fitted to the transmission case 21. It is arranged with respect to at least one of the swing links 18 of the crank mechanism 20. That is, among the first to sixth swing links 18A to 18F shown in the schematic diagram of FIG. 8A, the sensors 35A and 35B are connected to the first swing link 18A, the sixth swing link 18F, or both. Placed against. For this reason, the detection values of the sensors 35A and 35B are not affected as much as possible by the distortion or the like that the output shaft 3 receives.

  Signals indicating values detected by these two sensors 35A and 35B are sent to the management ECU 50 shown in FIG. FIG. 10 shows an example of detected values of the two sensors 35A and 35B obtained when the swing motion is performed to the maximum in the continuously variable transmission when no pipe expansion occurs, and values related to the detected values. It is a graph. The value indicated by the vertical axis is a value obtained by applying a bias to the detection values of the sensors 35A and 35B (bias detection value). The horizontal axis represents the swing range θ2 [deg] of the swing link 18. As shown in FIG. 10, the detected value A of the sensor 35A when the swing range θ2 is the maximum value θmax is obtained in the range of +1 to −1, and the detected value B of the sensor 35B is in the range of −1 to +1. The obtained detection values of the sensors 35A and 35B follow the swing motion of the swing link 18, and the average value of the detected values when the swing angle of the swing link 18 is 0 degree (swing center angle). It increases or decreases symmetrically about (bias detection value = 0).

  The management ECU 50 calculates a difference value (A−B) between the detection value A of the sensor 35A and the detection value B of the sensor 35B. As shown in FIG. 10, when the swing range θ2 is the maximum value θmax, the AB value is obtained in the range of +2 to −2, and the AB value follows the swing motion of the swing link 18, The swing link 18 increases or decreases symmetrically about the AB value (0 in the example shown in FIG. 10) when the swing angle is the half value θmax / 2 of the maximum angle θmax. Therefore, the management ECU 50 estimates the swing range θ2 of the swing link 18 based on the range from which the AB value is obtained from +2. For example, when the AB value is obtained in the range of +2 to 0, the management ECU 50 estimates that the swing range θ2 of the swing link 18 is θmax / 2 [deg] shown in FIG. When the value AB is only +2, the management ECU 50 estimates that the swing range θ2 of the swing link 18 is 0 [deg], that is, that the swing motion is not performed. Further, the management ECU 50 derives the eccentricity R1 corresponding to the estimated swing range θ2 of the swing link 18 from the specific relationship in the four-bar linkage mechanism of the continuously variable transmission 1 shown in FIG. Further, the management ECU 50 derives the input torque from the map based on the graph shown in FIG. 17 based on the eccentric amount R1 and the speed ratio i (= Nin / Nout) of the continuously variable transmission 1.

  In the above description with reference to FIG. 10, when the swing link 18 is fixed to the output shaft 3 by the one-way clutch 17 and torque is transmitted to the output shaft 3, no pipe expansion occurs in the swing link 18. Although it is assumed, pipe expansion will actually occur. FIG. 11 shows an example of detected values of the two sensors 35A and 35B obtained when the swing motion is maximally performed in the continuously variable transmission when the pipe expansion occurs, and values related to the detected values. It is a graph. The vertical and horizontal axes are the same as those in FIG. As shown in FIG. 11, when the swing range θ2 is the maximum value θmax, the detection value A of the sensor 35A is obtained in the range of +0.75 to −1.25, and the detection value B of the sensor 35B is −1. It is obtained in the range of 25 to +0.75. Therefore, even in the case shown in FIG. 11, the AB value is obtained in the range of +2 to −2 as in the case shown in FIG. 10, and the AB value is the swing of the swing link 18. According to the dynamic motion, the swing angle of the swing link 18 increases or decreases symmetrically about the AB value (0 in the example shown in FIG. 11) when the swing angle is the half value θmax / 2 of the maximum angle θmax. Therefore, the management ECU 50 can estimate the swing range θ2 of the swing link 18 on the basis of the range in which the AB value is obtained from +2 to what value even when the pipe expansion occurs. it can.

  The management ECU 50 calculates a half value ((A + B) / 2) of the sum of the detection value A of the sensor 35A and the detection value B of the sensor 35B, separately from the above-described estimation process of the swing range θ2. As shown in FIGS. 10 and 11, the (A + B) / 2 value is a constant value regardless of the swinging range θ2. However, when tube expansion occurs, the detection values of the sensors 35A and 35B generally decrease, and thus the (A + B) / 2 value also decreases. That is, since the (A + B) / 2 value decreases as the pipe expansion amount increases, the management ECU 50 estimates the pipe expansion amount from a map or a calculation formula based on the (A + B) / 2 value. A large amount of pipe expansion is equivalent to a large output torque transmitted to the output shaft 3. Therefore, the management ECU 50 derives the output torque from the expansion amount estimated based on the (A + B) / 2 value, using a map or a calculation formula.

  As described above, in the present embodiment, the eccentric amount R1 is derived from the swing range θ2 of the swing link 18, and the swing range θ2 of the swing link 18 is the difference value between the detection values of the sensors 35A and 35B. Estimated based on. As described above, the sensors 35 </ b> A and 35 </ b> B detect the distance to the outer peripheral surface of the swing link 18 including the raised portion 28, and do not detect the rotation state of the rotating member such as the rotation speed and the rotation angle. . Therefore, the error caused by the secular change or backlash of the rotating member in the detection values of the sensors 35A and 35B is very small. As described above, since the detection values obtained from the sensors 35A and 35B are highly accurate, it is possible to estimate the swing range θ2 with high accuracy and to derive the eccentric amount R1 with high accuracy. In addition, since the influence on the detection values of the sensors 35A and 35B due to the expansion of the swing link 18 is offset by the difference between the detection values, the expansion does not affect the estimation of the swing range θ2 of the swing link 18.

  In the present embodiment, the input torque is derived based on the highly accurate eccentric amount R1, and the highly accurate input torque can be derived. The detection values of the sensors 35A and 35B increase or decrease symmetrically about the average value of the respective detection values when the swing angle of the swing link 18 is 0 degree (swing center angle). The half value of the sum of is constant. The output torque is derived from the pipe expansion amount after estimating the pipe expansion amount based on the half value of the sum of the detected values. As described above, since the detection values obtained from the sensors 35A and 35B are highly accurate, and the detection values of the sensors 35A and 35B are values close to the output shaft 3, a more accurate output torque can be derived.

  The embodiments of the present invention have been described above, but various design changes can be made without departing from the scope of the present invention.

  For example, as shown in FIG. 12, the continuously variable transmission 1 is provided with a cylindrical surface 7e centered on the rotation center axis P1 on the cam disk 5 positioned substantially at the center of the input shaft 2, and the cylindrical surface 7e is a peripheral wall. You may comprise so that it may rotatably support via the intermediate bearing 26 in the partition part 21d extended from the part 21c. In this case, an intermediate bearing 27 that supports the output shaft 3 is provided on the output shaft 3 side of the partition wall portion 21d, and the sensors 35A and 35B are connected to the output shaft bearing 23 or the swing link 18 adjacent to the intermediate bearing 27. Arranged for at least one of them.

  In the above embodiment, the raised shape of the raised portion 28 is set so that the detection values of the sensors 35A and 35B obtained when the swing motion in the continuously variable transmission 1 is performed to the maximum indicate a sine wave. However, as shown in FIG. 13, the raised shape of the raised portion 28 may be set so that the detection values of the sensors 35A and 35B indicate a straight line. As shown in FIG. 14, the raised portion 28 in this case has a triangular side surface.

  Moreover, even if it is a structure which each sensor detects the distance to the outer peripheral surface of the rocking | fluctuation link 18 containing not only the structure by which the one protruding part 28 was allocated with respect to 35A and 35B but a several protruding part. good. In this configuration, as shown in FIG. 15, two ridges 28 arranged at different positions in the circumferential direction are provided in a part of the annular portion 18 d of the swing link 18 in the axial direction (output shaft 3 In the direction of the rotation center axis P4). The sensors 35A and 35B are arranged in the axial direction at the same circumferential position, the sensor 35A is provided corresponding to one raised portion 28, and the sensor 35B is provided corresponding to the other raised portion 28. In this case, the relationship between the shape of each raised portion and the positions of the sensors 35A and 35B can be set for each detection value. In addition, since the sensors 35A and 35B are arranged at the same circumferential position, the detection value is affected by the same expansion.

  Further, the detection values of the sensors 35A and 35B are not limited to the case where the amplitudes of the respective detection values are the same as shown in FIGS. 10 and 11, but may be different amplitudes as shown in FIG. . However, since the (A + B) / 2 value differs depending on the swing range θ2, a coefficient is used for estimating the expansion amount.

  In the above-described embodiment, the configuration in which the two sensors 35A and 35B are provided has been described as an example. However, three or more sensors are provided, and the detection values of two of the three or more sensors are used. The swing range θ2 may be estimated.

DESCRIPTION OF SYMBOLS 1 Continuously variable transmission 2 Input shaft 3 Output shaft 4 Turning radius adjustment mechanism 5 Cam disk 6 Rotating disk 6a Receiving hole 6b Inner tooth 7 Pinion shaft 7a Outer tooth 8 Differential mechanism 9 Sun gear 10 First ring gear 11 Second ring gear 12 Stage Pinion 12a Large-diameter portion 12b Small-diameter portion 13 Carrier 14 Adjustment 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 18 Oscillating link 18a Oscillating end 18b Projection piece 18c Through hole 18d Annular portion 19 Connecting pin 20 Lever crank mechanism 21 Transmission case 21a One end wall portion 21b Other end wall portion 21c Peripheral wall portion 22 Input shaft bearing 23 Output shaft bearing 26 Intermediate bearing 27 Intermediate bearing 28 Raised portion 31 Input shaft rotation Number sensor 33 Output shaft speed sensor 35A, 35B Gap sensor Sa)
50 Management ECU
P1 Rotation center axis P2 of the input shaft 2 Center P3 of the cam disk 5 Center P4 of the rotation disk 6 Rotation center axis P5 of the output shaft 3 Center Ra of the connecting pin 19 Rb A distance Rb between P1 and P2 A distance R1 between P2 and P3 P1 and P3 Distance (Eccentricity, turning radius of turning radius adjusting mechanism 4)
R2 Distance between P4 and P5 (length of swing link 18)
θ1 Phase of turning radius adjusting mechanism 4 θ2 Swing range of rocking link 18

Claims (8)

An input shaft to which the driving force of the driving source is transmitted;
An output shaft disposed parallel to the input shaft;
A rotation radius adjusting mechanism that is rotatable about the input shaft and capable of adjusting a rotation radius; and a swing link that is pivotally supported by the output shaft. A plurality of lever crank mechanisms that convert to the swing motion of
The swing link is fixed to the output shaft when the swing link is about to rotate to one side around the output shaft, and the swing shaft is fixed to the output shaft when the swing link is about to rotate to the other side. A continuously variable transmission comprising: a one-way rotation prevention mechanism that idles the swing link;
A raised portion inclined in the circumferential direction is provided on a part of the outer periphery of the swing link,
A plurality of detectors arranged on the outer peripheral side of the swing link and detecting a distance to the outer peripheral surface of the swing link including the raised portion;
The continuously variable transmission, wherein the difference between the values detected by any two of the plurality of detection units continuously changes according to the swing motion of the swing link. The continuously variable transmission according to claim 1,
The difference value between the values detected by each of the two arbitrary detection units is centered on the difference value when the swing angle of the swing link is a half value of the maximum angle according to the swing motion of the swing link. A continuously variable transmission that increases and decreases symmetrically. The continuously variable transmission according to claim 2,
The continuously variable transmission, wherein the sum of the values detected by each of the two arbitrary detectors is constant regardless of the swing motion of the swing link. A continuously variable transmission according to any one of claims 1 to 3,
The plurality of detection units are continuously variable transmissions arranged at positions where the lever crank mechanism does not cross a load direction applied to the output shaft via the swing link. A continuously variable transmission according to any one of claims 1 to 4,
The output shaft is supported by a bearing;
The said detection part is a continuously variable transmission arrange | positioned at the outer peripheral side of the said rocking | fluctuation link near the said bearing. A continuously variable transmission according to any one of claims 1 to 5,
The continuously variable transmission, wherein the plurality of detecting units are arranged at different positions along the circumferential direction of the swing link with respect to the raised portion provided on the outer periphery of the swing link. A continuously variable transmission according to any one of claims 1 to 5,
The raised portion has a plurality of raised portions having different phases with respect to the circumferential direction of the swing link, and the plurality of raised portions are respectively arranged at different positions in the axial direction of the output shaft,
Each of the plurality of detection units is a continuously variable transmission that is arranged in the axial direction corresponding to each of the plurality of raised portions and is disposed at the same position in the circumferential direction of the swing link. A continuously variable transmission according to any one of claims 1 to 7,
The two arbitrary detectors are configured with respect to a surface formed on a rotation center axis of the output shaft in a direction perpendicular to a load direction applied by the lever crank mechanism to the output shaft via the swing link. The continuously variable transmission is arranged at a symmetrical position in the circumferential direction of the swing link.

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