JP2015183777A - Continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a continuously variable transmission capable of supplying an appropriate quantity of lubricating oil to a connecting rod bearing.SOLUTION: A pinion shaft 7 includes a first oil passage 7c formed inside, and a second oil passage 7d communicating an inner circumferential surface with an outer circumferential surface. A rotary disc 6 includes a lubricating-oil supply hole 6c supplying lubricating oil supplied from the second oil passage 7d to a connecting rod bearing 16. A cam disc 5 includes a collar portion 5c covering an edge portion of an intake hole 6a. Part of the lubricating oil supplied from the second oil passage 7d is discharged from a discharge port formed by the edge portion of the intake hole 6a and the collar portion 5c.

Description

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

  Conventionally, an input shaft to which driving force from a main drive source (driving drive source) such as an engine is transmitted, an output shaft arranged in parallel with the rotation center axis of the input shaft, and a plurality of lever crank mechanisms are provided. A four-link mechanism type continuously variable transmission is known (for example, see Patent Document 1).

  In the continuously variable transmission described in Patent Document 1, the lever crank mechanism is provided with a rotating portion that can rotate integrally with an input shaft, and a rotating radius adjusting mechanism that can adjust the rotating radius of the rotating portion; A swing link provided with an end and pivotally supported on the output shaft, one end rotatably connected to the rotating portion of the turning radius adjusting mechanism, and the other end swings the swing link. And a connecting rod connected to the moving end.

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

  The turning radius adjusting mechanism includes a disc-shaped rotating part having a through hole formed eccentrically from the center, an internal gear attached to the inner peripheral surface of the through hole of the rotating part, and an internal tooth fixed to the input shaft. The first pinion meshing with the gear, the carrier to which the driving force from the auxiliary driving source (adjusting driving source) is transmitted, and each of which is pivotally supported by the carrier so as to rotate and revolve, and mesh with the internal gear. And the second pinion. 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.

  In addition to the one having the configuration shown in Patent Document 1, the turning radius adjusting mechanism is a disc-shaped cam portion that rotates integrally with the input shaft while being eccentric with respect to the input shaft, and is eccentric with respect to the cam portion. In some cases, a rotating part in which the connecting rod is rotatably fitted, a pinion shaft having a plurality of pinions in the axial direction, and a sub drive source for rotating the pinion shaft is there.

  In this turning radius adjusting mechanism, when the rotational speed of the input shaft rotated by the main drive source and the rotation speed of the carrier rotated by the sub drive source are the same, the eccentric amount of the center of the rotating portion with respect to the rotation center axis of the input shaft is maintained, The turning radius of the rotating part of the turning radius adjusting mechanism is also maintained constant. On the other hand, when the rotational speeds of the input shaft and the carrier are different, the amount of eccentricity of the center of the rotating portion with respect to the rotation center axis of the input shaft changes, and the turning radius of the rotating portion also changes.

  Therefore, this turning radius adjustment mechanism controls the rotation speed of the output shaft relative to the rotation speed of the input shaft by changing the turning radius, thereby changing the swing width of the swing end of the swing link and thus the gear ratio. To do.

  In addition, in this turning radius adjustment mechanism, the distance between the center of the equilateral triangle whose apex is the center of the three pinions and the rotational center axis of the input shaft is set equal to the distance between the center of the equilateral triangle and the center of the rotating part. doing.

  Therefore, this turning radius adjusting mechanism can make the eccentric amount “0” by superimposing the rotation center axis of the input shaft and the center of the rotating portion. 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 is not rotated.

  Further, in this turning radius adjusting mechanism, a cam portion is constituted by the carrier and the second pinion, and the driving force from the sub drive source is transmitted to the cam portion. The cam portion is set to have a different phase for each turning radius adjustment mechanism, that is, for each lever crank mechanism, and the cam portion makes a round in the circumferential direction of the input shaft.

  For this reason, the connecting rods externally fitted to the rotating portions of the respective turning radius adjusting mechanisms allow the respective swing links to transmit torque to the output shaft in order, so that the output shaft can be smoothly rotated.

  Further, a connecting rod bearing is disposed between the rotating portion of the turning radius adjusting mechanism and the connecting rod.

JP 2012-1048 A

  By the way, in a continuously variable transmission having such a configuration, a load is applied to the components of the lever crank mechanism in accordance with the rotation radius of the rotating part and the rotational speed of the engine that is the driving source for traveling, and friction is caused by the load. And heat is generated in the components of the lever crank mechanism. In particular, a large friction and heat are generated in the connecting rod bearing disposed between the rotating portion of the turning radius adjusting mechanism and the connecting rod fitted on the rotating portion.

  Therefore, in the conventional continuously variable transmission, the friction generated in the components of the lever crank mechanism is reduced and the heat is cooled by the lubricating oil.

  However, if the supply amount of lubricating oil is set in accordance with the rotation radius of the rotating part and the driving force output from the driving source for driving (for example, the engine speed) when the friction and heat become the largest, it is smaller than that. In the case of the turning radius or the number of revolutions, the amount of lubricating oil supplied may be excessive.

  If the lubricating oil is excessively supplied, the lubricating oil may become a resistance to the operation of the lever crank mechanism. In particular, in the connecting rod bearing, if the supplied lubricating oil is excessive, the lubricating oil may cause rolling resistance of the rolling elements disposed between the inner member and the outer member.

  The present invention has been made in view of the above points, and an object thereof is to provide a continuously variable transmission capable of supplying an appropriate amount of lubricating oil to a connecting rod bearing.

  In order to achieve the above object, a continuously variable transmission according to the present invention includes an input shaft to which a driving force of a traveling drive source is transmitted, an output shaft disposed in parallel with the rotation center axis of the input shaft, and an input shaft. A rotating radius adjusting mechanism that can rotate integrally with the rotating shaft, a swinging link provided with a swinging end and pivotally supported by the output shaft, and one end connected to the rotating radius adjusting mechanism, The lever has a connecting rod connected to the oscillating end, a lever crank mechanism for converting the rotational movement of the input shaft into the oscillating movement of the oscillating link, and the oscillating link on one side of the output shaft One direction to fix the swing link to the output shaft when trying to rotate in the direction of rotation, and idle the swing link relative to the output shaft when the swing link tries to rotate to the other side of the output shaft An anti-rotation mechanism, and an adjustment drive source for transmitting a driving force to the rotation radius adjustment mechanism; An oil pump that drives according to the driving force of the driving source for driving and discharges lubricating oil, and the turning radius adjusting mechanism is arranged coaxially with the input shaft, and transmits the driving force of the adjusting driving source. A pinion shaft is inserted at a position eccentric from the shaft, and a cam portion that rotates integrally with the input shaft while being eccentric with respect to the rotation center axis of the input shaft, and a cam portion is inserted at a position eccentric from the center. And a rotating portion that is rotatable in a state of being eccentric with respect to the cam portion, the outer peripheral surface of the pinion shaft is provided with external teeth, and the inner peripheral surface of the receiving hole of the rotating portion Are provided with internal teeth that mesh with the external teeth, and the rotation radius of the rotating portion around the rotation center axis of the input shaft is such that when the pinion shaft is rotated relative to the cam portion, the internal teeth and the external teeth are rotated. The rotating part is in phase with the cam part via the teeth. The connecting rod is connected to the turning radius adjusting mechanism by fitting one end of the connecting rod to the rotating part via the connecting rod bearing, and changing the turning radius of the rotating part. A continuously variable transmission having a variable speed ratio, formed on a rotation center axis of an input shaft inside a pinion shaft, and supplied with lubricating oil from one end of the pinion shaft by an oil pump And a second oil passage that is formed so as to communicate the inner peripheral surface and the outer peripheral surface of the pinion shaft, and that supplies the lubricating oil supplied through the first oil passage to the outer peripheral surface side of the pinion shaft, and a receiving hole A third oil passage that is formed so as to communicate between the inner peripheral surface and the outer peripheral surface of the first oil passage and that supplies the lubricating oil supplied via the second oil passage to the connecting rod bearing, and is supplied via the second oil passage. And a discharge oil passage for discharging a part of the lubricating oil to the outside of the lever crank mechanism, and the cam portion has a flange portion extending in the radial direction so as to cover the edge portion of the receiving hole, and is discharged The discharge port of the oil passage is formed by the edge of the receiving hole and the flange portion of the cam portion, and the flow rate of the lubricating oil discharged from the discharge oil passage depends on the relative phase between the rotating portion and the cam portion. It is characterized by changing.

  Thus, in the continuously variable transmission of the present invention, the pinion shaft is formed by the cylindrical member, and the inside is the first oil passage. Moreover, the 2nd oil path which connects the internal peripheral surface and an outer peripheral surface is formed in the pinion shaft. Further, a third oil passage is formed in the rotating portion to communicate the inner peripheral surface and the outer peripheral surface of the receiving hole through which the pinion shaft and the cam portion are inserted.

  The lubricating oil supplied by the oil pump through the first oil passage and the second oil passage is supplied to the outer peripheral surface of the pinion shaft, and then between the rotating portion and the connecting rod through the third oil passage. Is supplied to a connecting rod bearing.

  Further, the continuously variable transmission of the present invention has a discharge oil passage that discharges a part of the lubricating oil supplied through the second oil passage to the outside of the lever crank mechanism.

  Since the discharge port of the discharge oil passage is formed by the edge of the receiving hole of the rotating portion and the flange extending radially from the cam portion so as to cover the edge, the size of the discharge port Varies depending on the relative phase between the rotating portion and the cam portion. Therefore, the flow rate of the lubricating oil discharged from the discharging oil passage changes according to the relative phase between the rotating part and the cam part.

  The continuously variable transmission of the present invention includes such an oil passage together with an oil pump that is driven in conjunction with a driving source for travel, so that a lever crank mechanism can be used regardless of the rotation radius of the rotating portion, the engine speed, and the like. An appropriate amount of lubricating oil can be supplied to the connecting rod bearing, which is a component of the above.

  Further, in the continuously variable transmission according to the present invention, the lubricating oil that is mounted on the vehicle and is discharged in a relative phase between the rotating portion and the cam portion when the traveling speed of the vehicle reaches the maximum speed. It is preferable that the flow rate is minimized.

  When a continuously variable transmission is mounted on a vehicle, the radius of rotation of the rotating part and the engine speed at which the friction and heat generated in the connecting rod bearing, which is one of the components of the lever crank mechanism, are greatest. It becomes the rotation radius of the rotating part and the engine speed at which the speed becomes maximum.

  Therefore, if the rotational phase of the rotating part and the relative phase between the rotating part and the cam part corresponding to the rotational speed of the engine are configured so that the flow rate of the lubricating oil discharged from the discharging oil passage is minimized, the connecting When the lubricating oil is most required for the rod bearing, the amount of lubricating oil supplied to the connecting rod bearing through the first oil passage, the second oil passage, and the third oil passage can be maximized.

  In the continuously variable transmission of the present invention, the edge of the receiving hole is formed with a rotating part side hole through which the inner peripheral surface of the receiving hole communicates with the outside of the rotating part, and the lubricating oil is discharged. The flange portion of the cam portion is preferably formed so that the area covering the rotating portion side hole can be changed according to the relative phase between the rotating portion and the cam portion.

  Alternatively, in the continuously variable transmission according to the present invention, the edge of the receiving hole of the rotating part communicates with the inner peripheral surface of the receiving hole and the outside of the rotating part, and the rotating part side hole that discharges the lubricating oil. The cam part flange part is formed so as to cover the rotating part side hole part, and the cam part side hole part communicating with the rotary part side hole part is formed in the collar part of the cam part, and the rotating part It is preferable that the area where the side hole portion and the cam portion side hole portion communicate with each other changes according to the relative phase between the rotating portion and the cam portion.

  Thus, if the hole is formed at the edge of the receiving hole of the rotating part or the flange of the cam part and the discharge oil passage is formed using the hole, the rotating part and the cam part can be easily The flow rate of the lubricating oil discharged from the discharging oil passage can be changed in accordance with the relative phase of.

Sectional drawing which shows a part of continuously variable transmission which concerns on 1st Embodiment of this invention. Explanatory drawing which shows the structure of the lever crank mechanism of the continuously variable transmission of FIG. 1 from an axial direction. FIGS. 3A and 3B are explanatory diagrams showing changes in the rotation radius of the input side fulcrum of the lever crank mechanism of the continuously variable transmission of FIG. 1, 3A is “maximum”, 3B is “medium”, and 3C is rotation radius. “Small” and 3D indicate the case where the radius of rotation is “0”. FIG. 4 is an explanatory diagram showing changes in the swing range of the output side fulcrum with respect to changes in the rotation radius of the input side fulcrum of the lever crank mechanism of the continuously variable transmission of FIG. The movement range is “medium”, 4C indicates the swing range is “small”, and 4D indicates the swing range is “0”. The graph which shows the relationship between the amount of eccentricity of the lever crank mechanism of the continuously variable transmission of FIG. 1, and the rotation speed of an engine, and the quantity of required lubricating oil. FIG. 6 is an explanatory view showing the opening degree of the discharge oil passage at each eccentric amount of the lever crank mechanism of the continuously variable transmission of FIG. 1 from the direction intersecting the axis, where 6A is the rotation radius of the input side fulcrum and “6B” The turning radius is “large”, 6C is the turning radius is “small”, and 6D is the turning radius is “0”. FIG. 7 is an explanatory view showing the opening degree of the discharge oil passage from the axial direction at each eccentric amount of the lever crank mechanism of the continuously variable transmission of FIG. 1, where 7A is the rotation radius of the input side fulcrum and 7B is the rotation radius Is “large”, 7C is the rotation radius is “small”, and 7D is the rotation radius is “0”. It is explanatory drawing which shows the opening degree of the discharge | emission oil path in each eccentric amount of the lever crank mechanism of the continuously variable transmission of 2nd Embodiment of this invention from the direction which cross | intersects an axis | shaft, 8A is the rotation radius of an input side fulcrum " “Maximum”, 8B indicates a case where the turning radius is “large”, 8C indicates a case where the turning radius is “small”, and 8D indicates a case where the turning radius is “0”. It is explanatory drawing which shows the opening degree of the discharge oil path from the axial direction in each eccentric amount of the lever crank mechanism of the continuously variable transmission of 2nd Embodiment of this invention, 9A is the rotation radius of an input side fulcrum "maximum" , 9B shows a case where the turning radius is “large”, 9C shows a turning radius of “small”, and 9D shows a case where the turning radius is “0”.

  Hereinafter, embodiments of a continuously variable transmission according to the present invention will be described with reference to the drawings. The continuously variable transmission of the present embodiment is a four-bar linkage type continuously variable transmission, and outputs with a gear ratio h (h = rotational speed of the input shaft / rotational speed of the output shaft) set to infinity (∞). This is a kind of transmission that can make the rotational speed of the shaft "0", so-called IVT (Infinity Variable Transmission). Although this embodiment is an embodiment in the case where the continuously variable transmission is mounted on a vehicle, the continuously variable transmission of the present invention can be mounted on other vehicles and unmanned vehicles such as ships. .

[First Embodiment]
With reference to FIGS. 1-6, the continuously variable transmission 1 of 1st Embodiment is demonstrated.

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

  As shown in FIG. 1, the continuously variable transmission 1 of the present embodiment includes an input unit 2, an output shaft 3 arranged in parallel with the rotation center axis P <b> 1 of the input unit 2, and a rotation center axis P <b> 1 of the input unit 2. And six turning radius adjusting mechanisms 4 provided on the top.

  The input unit 2 rotates around the rotation center axis P <b> 1 by transmitting a driving force from an engine ENG (traveling drive source) that is a main drive source. In addition, as a main drive source, you may use an electric motor other than an internal combustion engine.

  The output shaft 3 transmits a rotational driving force to driving wheels (not shown) of the vehicle via a differential gear (not shown). A propeller shaft may be provided instead of the differential gear.

  The turning radius adjusting mechanism 4 includes a cam disk 5 (cam part) provided on the rotation center axis P <b> 1 of the input unit 2 and a rotating disk 6 (rotating part) that is rotatably fitted on the cam disk 5. Have.

  The cam disks 5 have a disk shape, and are provided in pairs so that they can rotate integrally with the input unit 2 while being eccentric with respect to the rotation center axis P1 of the input unit 2. Each set of cam disks 5 is set so as to have a phase difference of 60 °, and is arranged so that the six sets of cam disks 5 make a round in the circumferential direction of the rotation center axis P1 of the input unit 2.

  The cam disk 5 is formed with a through hole 5 a that penetrates in the direction of the rotation center axis P <b> 1 of the input unit 2 and is formed at a position eccentric with respect to the center P <b> 2 of the cam disk 5. Further, the cam disk 5 communicates with the outer peripheral surface of the cam disk 5 and the inner peripheral surface of the through hole 5a in a region opposite to the center P2 of the cam disk 5 across the rotation center axis P1 of the input portion 2. A notch hole 5b is formed.

  A set of two cam disks 5 is fixed with bolts (not shown). Further, one of the two cam disks 5 is formed integrally with the other of the other two cam disks 5 of the adjacent turning radius adjusting mechanism 4 to form an integral cam portion. Yes. The cam disk 5 located closest to the engine ENG among the cam disks 5 is formed integrally with the input unit 2. In this way, the input unit 2 and the plurality of cam disks 5 constitute an input shaft (camshaft).

  The two cam disks 5 may be fixed by other means instead of bolts. The integral cam portion may be formed by integral molding, or may be integrated by welding two cam disks 5. In addition, as a method of integrally forming the cam disk 5 and the input portion 2 that are closest to the engine ENG, the cam disc 5 and the input portion 2 may be integrally formed. May be used.

  As shown in FIG. 2, the rotary disk 6 has a disk shape in which a receiving hole 6 a is provided at a position eccentric from the center P <b> 3, and is provided to be rotatable with respect to the rotation center axis P <b> 1 of the input unit 2. . A set of cam disks 5 is rotatably fitted in the receiving holes 6a. Further, as shown in FIG. 1, an internal tooth 6 b is provided in the receiving hole 6 a of the rotating disk 6 at a position between the pair of cam disks 5.

  Further, the receiving hole 6a of the rotating disk 6 has a distance Rx from the rotation center axis P1 of the input portion 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 center of the rotating disk 6. The cam disk 5 is eccentric so that the distance Ry to P3 is the same.

  The input shaft configured by the input unit 2 and the plurality of cam disks 5 includes an insertion hole 50 configured by connecting through holes 5 a of the cam disk 5. Thereby, the input shaft has a hollow shaft shape in which one end opposite to the engine ENG is open and the other end is closed.

  In the insertion hole 50, the pinion shaft 7 is arranged concentrically with the rotation center axis P1 so as to be rotatable relative to the input shaft.

  The pinion shaft 7 has a pinion 7 a at a position corresponding to the internal teeth 6 b of the rotary disk 6. Further, the pinion shaft 7 is positioned between adjacent pinions 7 a in the direction of the rotation center axis P <b> 1 of the input unit 2, and a pinion bearing 7 b is provided. The pinion shaft 7 supports the input shaft via the pinion bearing 7b.

  The pinion 7 a is formed integrally with the shaft portion of the pinion shaft 7. The pinion 7 a meshes with the internal teeth 6 b of the rotating disk 6 through the notch hole 5 b of the cam disk 5. The pinion 7a may be configured separately from the pinion shaft 7 and connected to the pinion shaft 7 by spline coupling. In the present embodiment, the term “pinion 7 a” is defined as including the pinion shaft 7.

  The pinion shaft 7 is connected to a differential mechanism 8 constituted by a planetary gear mechanism or the like.

  As shown in FIG. 1, the differential mechanism 8 is configured as a planetary gear mechanism, for example, and includes a sun gear 9, a first ring gear 10 connected to an input shaft configured by the input unit 2 and a plurality of cam disks 5. A stepped pinion 12 comprising a second ring gear 11 connected to the pinion shaft 7, a large diameter portion 12 a meshing with the sun gear 9 and the first ring gear 10, and a small diameter portion 12 b meshing with the second ring gear 11 is rotated and rotated. It has a carrier 13 that is pivotably supported.

  The sun gear 9 is connected to a rotation shaft 14 a of an actuator 14 (adjustment drive source) that is a sub drive source for the pinion shaft 7, and a driving force is transmitted from the actuator 14. Therefore, the driving force of the actuator 14 is also transmitted to the pinion 7 a via the differential mechanism 8.

  When the rotation speed of the pinion shaft 7 is the same as the rotation speed of the input unit 2, the sun gear 9 and the first ring gear 10 rotate at the same speed. As a result, the four elements of the sun gear 9, the first ring gear 10, the second ring gear 11, and the carrier 13 are locked so that they cannot rotate relative to each other, and the pinion shaft 7 connected to the second ring gear 11 is the same as the input unit 2. Rotates at speed.

  When the rotational speed of the pinion shaft 7 is made slower than the rotational speed of the input unit 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 (first When j is the number of teeth of the ring gear 10 / the number of teeth of the sun gear 9, the number of rotations of the carrier 13 is (j · NR1 + Ns) / (j + 1). 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)}.

  That is, when there is a difference between the rotational speed of the input unit 2 and the rotational speed of the pinion shaft 7, the driving force transmitted from the actuator 14 transmitted through the internal teeth 6 b of the rotating disk 6 that meshes with the pinion 7 a of the pinion shaft 7. Thus, the rotating disk 6 rotates the periphery of the cam disk 5 around the center P2 of the cam disk 5.

  Incidentally, as shown in FIG. 2, the rotating disk 6 rotates with respect to the cam disk 5 from the rotation center axis P <b> 1 of the input unit 2 to the center P <b> 2 of the cam disk 5 and the center P <b> 2 of the cam disk 5. It is eccentric so that the distance Ry to the center P3 of the disk 6 is the same.

  Therefore, the center P3 of the rotary disk 6 is positioned on the same line as the rotation center axis P1 of the input unit 2, and the distance between the rotation center axis P1 of the input unit 2 and the center P3 of the rotary disk 6 (of the rotation radius adjusting mechanism 4). The rotation radius), that is, the eccentricity R1 can be set to “0”.

  At the periphery of the rotary disk 6, there is a large-diameter input-side annular portion 15 a at one end (on the input portion 2 side), and at the other end (output shaft 3), the diameter of the input-side annular portion 15 a is larger. A connecting rod 15 having a small-diameter output-side annular portion 15b is rotatably connected.

  The input side annular portion 15a of the connecting rod 15 is rotatably fitted to the rotary disk 6 via connecting rod bearings 16 each consisting of a set of two ball bearings arranged in the axial direction.

  Six swing links 18 are pivotally supported on the output shaft 3 in correspondence with the connecting rod 15 via a one-way clutch 17 (one-way rotation prevention mechanism).

  The one-way clutch 17 is provided between the swing link 18 and the output shaft 3, and the swing link 18 tends to rotate relative to the output shaft 3 on one side about the rotation center axis P <b> 5 of the output shaft 3. In this case, the swing link 18 is fixed to the output shaft 3 (fixed state), and the swing link 18 is idled with respect to the output shaft 3 (idle state) when relative rotation is to be made on the other side. ).

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

  By inserting the connecting pin 19 as a swing shaft into the insertion hole 18c and the output side annular portion 15b, the connecting rod 15 and the swing link 18 are connected so as to be relatively rotatable.

  In the continuously variable transmission 1 of the present embodiment, a lever crank mechanism 20 is configured by the turning radius adjusting mechanism 4 having the above-described configuration, the swing link 18, and the connecting rod 15.

  The lever crank mechanism 20 and the one-way clutch 17 are housed in a transmission case 21. Below the transmission case 21, lubricating oil forms an oil reservoir.

  The swing link 18 is disposed such that the swing end portion 18a is immersed in an oil reservoir of lubricating oil collected below the transmission case 21.

  Therefore, when the lever crank mechanism 20 is driven, the oscillating end portion 18a is lubricated by the oil reservoir, and the lubricating oil in the oil reservoir is lifted up by the oscillating motion of the oscillating link 18, so that The parts can be lubricated.

  Further, the transmission case 21 is arranged so as to be spaced from the 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 lever crank mechanism 20 and the one-way clutch 17. It is formed by a peripheral wall portion 21c that covers and connects the outer edge of the one end wall portion 21a and the outer edge of the other end wall portion 21b.

  An opening for pivotally supporting the input shaft and an opening for pivotally supporting the output shaft 3 are formed in the one end wall portion 21a and the other end wall portion 21b. The shaft bearing 22 and the output shaft bearing 23 are fitted.

  The transmission case 21 includes an oil pump (not shown) therein. In the oil pump, the amount of lubricating oil discharged increases in conjunction with an increase in the rotational speed of the engine ENG, which is a driving source for traveling. Lubricating oil is supplied to one end side of the input shaft by this oil pump.

  In the present embodiment, the one provided with the six lever crank mechanisms 20 has been described. However, the number of lever crank mechanisms in the continuously variable transmission of the present invention is not limited to that number. For example, five or less lever crank mechanisms may be provided, or seven or more lever crank mechanisms may be provided. May be.

  Further, in the present embodiment, the input shaft 2 and the plurality of cam disks 5 constitute an input shaft, and the input shaft is provided with the insertion hole 50 configured by connecting the through holes 5 a of the cam disk 5. . However, the input shaft in the continuously variable transmission of the present invention is not limited to that configured as described above.

  For example, the input part is configured in a hollow shaft shape having an insertion hole so that one end is opened, and the through hole is formed to be larger than that of the present embodiment so that the input part can be inserted into a disc-shaped cam disk. The cam disk may be splined to the outer peripheral surface of the input portion configured in a hollow shaft shape.

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

  Further, in the present embodiment, the one-way rotation prevention mechanism using the one-way clutch 17 has been described. However, the one-way rotation prevention mechanism in the continuously variable transmission of the present invention is not limited to the one-way clutch, and for example, the rotation direction of the swing link capable of transmitting torque from the swing link to the output shaft can be switched. A two-way clutch may be used.

  Next, the lever crank mechanism 20 of the continuously variable transmission according to this embodiment will be described with reference to FIGS.

  As shown in FIG. 1, the continuously variable transmission 1 of the present embodiment includes a total of six lever crank mechanisms 20 (four-bar linkage mechanisms). As shown in FIG. 2, the lever crank mechanism 20 includes a connecting rod 15, a swing link 18, and a rotating radius adjusting mechanism 4 having a rotating disk 6 and having an adjustable rotating radius. The lever crank mechanism 20 converts the rotational motion of the input shaft into the swing motion of the swing link 18.

  In this lever crank mechanism 20, when the rotation radius (eccentricity R1) of the center P3 (input side fulcrum) of the rotary disk 6 of the rotation radius adjusting mechanism 4 is not "0", the input unit 2 and the pinion shaft 7 are the same. When rotating at a speed, each connecting rod 15 pushes the swing end 18a between the input unit 2 and the output shaft 3 toward the output shaft 3 or pulls it toward the input unit 2 while changing the phase. The rocking link 18 is rocked by alternately repeating.

  Since the one-way clutch 17 is provided between the swing link 18 and the output shaft 3, the connecting rod 15 causes the swing link 18 to rotate to the one side with respect to the output shaft 3. When rotating at a speed exceeding the speed, the swing link 18 is fixed to the output shaft 3 and transmits torque to the output shaft 3. On the other hand, when the swing link 18 rotates to the other side with respect to the output shaft 3, the swing link 18 idles with respect to the output shaft 3, and no torque is transmitted to the output shaft 3.

  In the continuously variable transmission 1 of the present embodiment, the turning radius adjusting mechanisms 4 of the six lever crank mechanisms 20 are arranged with phases shifted by 60 degrees, so that the output shaft 3 has six lever cranks. The mechanism 20 is rotated in order.

  FIG. 3 is a diagram showing the positional relationship between the pinion shaft 7 and the rotating disk 6 in a state where the rotating radius (the eccentric amount R1) of the center P3 (input side fulcrum) of the rotating disk 6 of the rotating radius adjusting mechanism 4 is changed. is there.

  FIG. 3A shows a state in which the amount of eccentricity R1 is set to “maximum”, and the pinion shaft 7 so that the rotation center axis P1 of the input unit 2, the center P2 of the cam disk 5, and the center P3 of the rotation disk 6 are aligned. And the rotating disk 6 are positioned. In this case, the gear ratio h is “minimum”.

  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 shows a state in which the eccentric amount R1 is set to be “small” which is further smaller than that in FIG. The gear ratio h is “medium” which is larger than the gear ratio h in FIG. 3A in FIG. 3B and “large” which is larger than the gear ratio h in FIG. 3B in FIG.

  FIG. 3D shows a state where the amount of eccentricity R1 is “0”, and the rotation center axis P1 of the input unit 2 and the center P3 of the rotary disk 6 are located concentrically. In this case, the gear ratio h is “infinity (∞)”.

  FIG. 4 is a diagram showing the relationship between the rotation radius (eccentricity R1) of the center P3 (input side fulcrum) of the rotary disk 6 of the rotary radius adjusting mechanism 4 and the swing range θ2 of the swing motion of the swing link 18. It is.

  4A shows the case where the eccentric amount R1 is “maximum” in FIG. 3A (when the gear ratio h is “minimum”), and FIG. 4B shows the case where the eccentric amount R1 is “medium” in FIG. 4C shows the case where the eccentric amount R1 is “small” in FIG. 3C (when the gear ratio h is “large”), FIG. 4D shows the amount of eccentricity R1 shown in FIG. Is “0” (when the gear ratio h is “infinity (∞)”).

  Here, R2 is the length of the swing link 18. More specifically, R2 is the distance from the rotation center axis P5 of the output shaft 3 to the connection point between the connecting rod 15 and the swinging end 18a, that is, the center of the connection pin 19 (output-side fulcrum P4). . Θ1 is the phase of the rotating disk 6 of the turning radius adjusting mechanism 4.

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

  Next, a structure for supplying lubricating oil to the connecting rod bearing 16 of the lever crank mechanism 20 of the continuously variable transmission 1 of the present embodiment will be described in detail with reference to FIGS. 1 and 5 to 7.

  As shown in FIG. 1, the pinion shaft 7 is formed as a cylindrical member having a first oil passage 7c formed on the rotation center axis P1 of the input shaft. Lubricating oil discharged from an oil pump (not shown) flows into the first oil passage 7c from one end side (left side in FIG. 1) of the pinion shaft 7.

  Further, the pinion shaft 7 is formed with a second oil passage 7d formed at a position corresponding to the pinion bearing 7b so as to communicate the inner peripheral surface and the outer peripheral surface of the pinion shaft 7. Lubricating oil flows into the second oil passage 7d from the first oil passage 7c, and the lubricating oil is supplied to the outer peripheral surface side of the pinion shaft 7.

  The lubricating oil supplied from the second oil passage 7d to the outer peripheral surface side of the pinion shaft 7 is supplied to a pinion bearing 7b disposed adjacent to the pinion 7a. After that, the lubricating oil is connected to the connecting rod by centrifugal force through the gaps and side surfaces of the plurality of cam disks 5 constituting the camshaft and the lubricating oil supply hole 6c (third oil passage) formed in the rotating disk 6. It is supplied to the bearing 16.

  The inlet through which the lubricating oil flows into the lubricating oil supply hole 6c is formed on the inner peripheral surface of the receiving hole 6a of the rotating disk 6 through which the cam disk 5 and the pinion shaft 7 are inserted. On the other hand, the outlet from which the lubricating oil flows out from the lubricating oil supply hole 6 c is formed on the outer peripheral surface of the rotating disk 6. Lubricating oil flowing out from the outlet is supplied to a connecting rod bearing 16 disposed between the rotating disk 6 and a connecting rod 15 fitted on the rotating disk 6.

  Incidentally, as shown by the solid line and the broken line in the graph of FIG. 5, in the continuously variable transmission 1 of the present embodiment, the rotational radius (eccentricity R1) of the center P3 (input side fulcrum) of the rotary disk 6 of the rotational radius adjusting mechanism 4. ) And the driving force (the rotational speed of the engine ENG) output from the driving source for travel increases, the friction and heat generated in the components on the input shaft side of the lever crank mechanism 20 such as the pinion bearing 7b and the connecting rod bearing 16 are reduced. The amount of lubricating oil required for cooling the water increases.

  The amount of lubricating oil supplied to the component on the input shaft side of the lever crank mechanism 20 by the oil pump is the amount of eccentricity R1 where the friction and heat generated in the component members of the lever crank mechanism 20 are the largest and the rotational speed of the engine ENG. In this case, it is preferable to set a sufficient amount.

  Specifically, the setting is based on the case where the vehicle speed of the vehicle equipped with the continuously variable transmission 1 is the maximum speed (in the graph, when R1 = large and the engine speed is maximum). Is preferred.

  However, as indicated by the alternate long and short dash line in the graph of FIG. 5, the general oil pump used in the continuously variable transmission 1 of the present embodiment has a supply amount of lubricating oil proportional to the rotational speed of the engine ENG. To increase. Therefore, when the amount of lubricating oil discharged from the oil pump is adjusted so as to be optimal in a state where the vehicle speed reaches the maximum speed, the lever crank mechanism 20 is used when the eccentric amount R1 and the engine ENG rotation speed are small. The amount of lubricating oil supplied will be excessive.

  If the lubricating oil is supplied excessively, the lubricating oil may become a resistance to the operation of the component member on the input shaft side of the lever crank mechanism 20.

  In particular, the connecting rod bearing 16 disposed between the rotating disk 6 and the input side annular portion 15a of the connecting rod 15 generates a large amount of friction and heat, and therefore requires a lot of lubricating oil. Therefore, when the amount of eccentricity R1 and the rotational speed of the engine ENG are small, the lubricating oil is particularly easily supplied excessively.

  When the lubricating oil supplied to the connecting rod bearing 16 of the lever crank mechanism 20 becomes excessive, the lubricating oil is interposed between the inner member and the outer member (in this embodiment, the outer peripheral surface of the rotating disk 6 and the connecting rod 15 There is a possibility that the rolling resistance of the rolling elements arranged between the input side annular portion 15a and the inner peripheral surface of the input side annular portion 15a may become rolling resistance.

  Therefore, the continuously variable transmission 1 of the present embodiment includes a mechanism that adjusts the amount of lubricating oil supplied to the connecting rod bearing 16 of the lever crank mechanism 20 in accordance with the eccentric amount R1. In the following, the mechanism will be described in detail.

  As shown in FIG. 6, at the edge of the receiving hole 6a of the rotating disk 6, a rotating disk side notch 6d (rotating part side) communicating the inner peripheral surface of the receiving hole 6a and the outside (side surface) of the rotating disk 6 is provided. Hole) is formed. The rotating disk side notch 6d is not shown in FIG.

  The cam disk 5 has a flange 5c extending in the radial direction so as to cover the edge of the rotating disk 6 at a position that does not overlap the rotating disk 6 in a direction intersecting the rotation center axis P1 of the input shaft. .

  As shown in FIG. 7, the rotary disk side notch 6d is formed at the edge of the receiving hole 6a. The shape of the outer periphery of the rotating disk side cutout 6 d is a shape that matches the semicircle formed toward the outer periphery of the rotating disk 6.

  The shape of the outer periphery of the flange portion 5 c of the cam disk 5 is a shape that matches the circle whose center is eccentric from the center P <b> 2 of the cam disk 5. That is, the flange 5c has a different distance from the center P2 of the cam disk to the outer periphery for each phase.

  Therefore, the area (region) in which the flange portion 5c covers the rotating disk side notch portion 6d changes according to the relative phase between the rotating disk 6 and the cam disk 5 (that is, the eccentric amount R1).

  In the continuously variable transmission 1 according to the present embodiment, since the discharge oil passage is formed by the rotary disk side cutout portion 6d and the flange portion 5c, the opening degree of the discharge port of the discharge oil passage is determined by the rotation disk 6 And the cam disk 5 change in accordance with the relative phase (that is, the eccentric amount R1). Therefore, the flow rate of the lubricating oil discharged from the discharging oil passage also changes according to the relative phase between the rotating disk 6 and the cam disk 5.

  Specifically, as shown in FIG. 7A, when the relative phase is a phase where the eccentricity R1 is “maximum”, only a part of the notch 6d on the rotating disk side is covered with the flange 5c.

  In this case, as shown in FIG. 6A, a part of the lubricating oil supplied from the second oil passage to the outer peripheral surface of the pinion shaft 7 is a discharge oil formed by the rotary disk side notch portion 6d and the flange portion 5c. Only the remaining lubricating oil is discharged from the path and supplied to the connecting rod bearing 16 through the lubricating oil supply hole 6c.

  As shown in FIG. 7B, when the relative phase is a phase where the eccentric amount R1 is “large” (the phase where the traveling speed of the vehicle is the maximum speed), the rotary disk side notch portion 6d is entirely formed by the flange portion 5c. Covered.

  In this case, as shown in FIG. 6B, the lubricating oil supplied from the second oil passage to the outer peripheral surface of the pinion shaft 7 is discharged from the discharge oil passage formed by the rotating disk side cutout portion 6d and the flange portion 5c. Instead, all the lubricating oil is supplied to the connecting rod bearing 16 via the lubricating oil supply hole 6c.

  As shown in FIG. 7C, when the relative phase is a phase at which the eccentricity R1 becomes “small”, the rotary disk side notch 6d is covered by the flange 5c at least half.

  In this case, as shown in FIG. 6C, an amount less than half of the lubricating oil supplied from the second oil passage to the outer peripheral surface of the pinion shaft 7 is discharged by the rotating disk side notch 6d and the flange 5c. Only the remaining lubricating oil is discharged from the oil passage and supplied to the connecting rod bearing 16 through the lubricating oil supply hole 6c.

  As shown in FIG. 7D, when the relative phase is a phase where the eccentricity R1 is “0”, about half of the rotating disk side cutout 6d is covered with the flange 5c.

  In this case, as shown in FIG. 6D, about half of the amount of lubricating oil supplied from the second oil passage to the outer peripheral surface of the pinion shaft 7 is discharged by the rotary disk side notch 6d and the flange 5c. Only the remaining lubricating oil is discharged from the oil passage and supplied to the connecting rod bearing 16 through the lubricating oil supply hole 6c.

  The continuously variable transmission 1 according to the present embodiment includes the first oil passage 7c, the second oil passage 7d, the lubricating oil supply hole 6c (third oil passage), and the discharge oil passage, and thus the lubricating oil supply hole 6c. The amount of the lubricating oil supplied to the connecting rod bearing 16 via changes in accordance with the change in the eccentric amount R1. Therefore, an appropriate amount of lubricating oil can be supplied to the connecting rod bearing 16 of the lever crank mechanism 20.

[Second Embodiment]
The continuously variable transmission according to this embodiment will be described with reference to FIGS. However, the continuously variable transmission according to the present embodiment differs from the continuously variable transmission according to the first embodiment only in the shapes of the cam disk and the rotating disk, and only these will be described in detail. In addition, the same reference numerals are given to the same components as those of the continuously variable transmission according to the first embodiment, and descriptions thereof are omitted.

  As shown in FIG. 8, a rotating disk side notch 6 e that communicates the inner peripheral surface of the receiving hole 6 a and the outside of the rotating disk 6 is formed at the edge of the receiving hole 6 a of the rotating disk 6.

  The cam disk 5 has a flange portion 5d extending in the radial direction so as to cover the edge of the rotating disk 6 at a position that does not overlap the rotating disk 6 in a direction intersecting the rotation center axis P1 of the input shaft. . Further, a cam disk side cutout portion 5e (cam portion side cutout portion) is formed at the edge portion of the flange portion 5d.

  As shown in FIG. 9, the shape of the outer periphery of the rotary disk side notch 6e is a circle eccentric from the center P2 of the cam disk 5, or the circle is offset to the opposite side across the center P2 of the cam disk 5. It has a shape that matches the centered circle.

  The shape of the outer periphery of the flange 5d of the cam disk 5 is such that the center thereof is the center P2 of the cam disk 5 and coincides with a circle having a larger radius than the receiving hole. The shape of the cam disk side cutout 5 e is a shape that matches the semicircle formed toward the inner peripheral side of the cam disk 5.

  Therefore, the flange 5d covers the rotating disk side notch 6e (the cam disk side notch 5e and the rotating disk side notch 6e in accordance with the relative phase between the rotating disk 6 and the cam disk 5 (that is, the eccentric amount R1). The area that communicates with) changes.

  In the continuously variable transmission according to the present embodiment, since the discharge oil passage is formed by the rotary disk side cutout 6e and the flange portion 5d, the opening degree of the discharge port of the discharge oil passage is the same as that of the rotary disk 6. It changes in accordance with the relative phase with respect to the cam disk 5 (that is, the eccentric amount R1). Therefore, the flow rate of the lubricating oil discharged from the discharging oil passage also changes according to the relative phase between the rotating disk 6 and the cam disk 5.

  Specifically, as shown in FIG. 9A, when the relative phase is a phase at which the eccentric amount R1 is “maximum”, the rotating disk side cutout portion 6e is only part of the cam disk side cutout portion 5e. Communicate with.

  In this case, as shown in FIG. 8A, a part of the lubricating oil supplied from the second oil passage to the outer peripheral surface of the pinion shaft 7 is a discharge oil formed by the rotary disk side notch portion 6e and the flange portion 5d. Only the remaining lubricating oil is discharged from the path and supplied to the connecting rod bearing 16 through the lubricating oil supply hole 6c.

  As shown in FIG. 9B, when the relative phase is the phase at which the eccentric amount R1 is “large” (the phase at which the vehicle travel speed is the maximum speed), the rotating disk side notch 6e is entirely formed by the flange 5d. Covered.

  In this case, as shown in FIG. 8B, the lubricating oil supplied from the second oil passage to the outer peripheral surface of the pinion shaft 7 is discharged from the discharge oil passage formed by the rotating disk side cutout portion 6e and the flange portion 5d. Instead, all the lubricating oil is supplied to the connecting rod bearing 16 via the lubricating oil supply hole 6c.

  As shown in FIG. 9C, when the relative phase is a phase at which the eccentricity R1 becomes “small”, about half of the rotary disk side cutout portion 6e communicates with the cam disk side cutout portion 5e of the flange portion 5d.

  In this case, as shown in FIG. 8C, about half of the amount of lubricating oil supplied from the second oil passage to the outer peripheral surface of the pinion shaft 7 is discharged by the rotary disk side notch 6e and the flange 5d. Only the remaining lubricating oil is discharged from the oil passage and supplied to the connecting rod bearing 16 through the lubricating oil supply hole 6c.

  As shown in FIG. 9D, when the relative phase is a phase where the eccentricity R1 is “0”, more than half of the rotating disk side cutout portion 6e communicates with the cam disk side cutout portion 5e of the flange portion 5d.

  In this case, as shown in FIG. 8D, more than half of the amount of lubricating oil supplied from the second oil passage to the outer peripheral surface of the pinion shaft 7 is discharged by the rotary disk side notch 6e and the flange 5d. Only the remaining lubricating oil is discharged from the oil passage and supplied to the connecting rod bearing 16 through the lubricating oil supply hole 6c.

  The continuously variable transmission 1 according to the present embodiment includes the first oil passage 7c, the second oil passage 7d, the lubricating oil supply hole 6c (third oil passage), and the discharge oil passage, and thus the lubricating oil supply hole 6c. The amount of the lubricating oil supplied to the connecting rod bearing 16 via changes in accordance with the change in the eccentric amount R1. Therefore, an appropriate amount of lubricating oil can be supplied to the connecting rod bearing 16 of the lever crank mechanism 20.

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

  For example, the shape of the flange portion and the rotating portion side hole portion of the present invention is not limited to the shape as shown in the above embodiment, and is formed according to the relative phase between the cam portion and the rotating portion. It is sufficient that the opening degree of the discharge port of the discharge oil passage is different. For example, the cam part side hole part and the rotating part side hole part are not necessarily notched.

DESCRIPTION OF SYMBOLS 1 ... Continuously variable transmission, 2 ... Input part, 3 ... Output shaft, 4 ... Turning radius adjustment mechanism, 5 ... Cam disk (cam part), 5a ... Through-hole, 5b ... Notch hole, 5c, 5d ... Gutter part, 5e: Cam disk side notch (cam part side hole), 6: Rotating disk (rotating part), 6a ... Receiving hole, 6b ... Internal tooth, 6c ... Lubricating oil supply hole (third oil passage), 6d, 6e Rotating disk side notch (rotating part side hole), 7 ... Pinion shaft, 7a ... Pinion, 7b ... Pinion bearing, 7c ... First oil passage, 7d ... Second oil passage, 8 ... Differential mechanism, 14a ... Rotating shaft, 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 ... actuator (drive source for adjustment), 15 ... Connecting rod, 15a ... Input side annular part, 15b ... Output side ring , 16 ... Connecting rod bearing, 17 ... One-way clutch (one-way rotation prevention mechanism), 18 ... Swing link, 18a ... Swing end, 18b ... Projection piece, 18c ... Insertion hole, 19 ... Connecting pin, 20 ... lever crank mechanism, 21 ... transmission case, 21a ... one end wall part, 21b ... other end wall part, 21c ... peripheral wall part, 22 ... bearing, 50 ... insertion hole, ENG ... engine (driving drive source), h ... Transmission ratio, P1... Rotation axis of input shaft, P2... Center of cam disk 5, P3... Center of rotation disk 6 (input side fulcrum), P4. 3 rotation center axis, Rx... P1 and P2 distance, Ry... P2 and P3 distance, R1... P1 and P3 distance (eccentricity, rotation radius of the center of the rotating disk 6 (input side fulcrum P3)), R2. ... Distance between P4 and P5 The length of the click 18), .theta.1 ... of the rotary disc 6 phase, .theta.2 ... swing range of the swing link 18.

Claims (4)

An input shaft to which the driving force of the driving source for traveling is transmitted;
An output shaft disposed parallel to the rotation center axis of the input shaft;
A turning radius adjusting mechanism capable of rotating integrally with the input shaft, a swinging link provided with a swinging end portion and pivotably supported by the output shaft, and one end portion of the turning radius adjusting mechanism A lever crank having a connecting rod connected to the oscillating end at the other end, and converting the rotational motion of the input shaft into the oscillating motion of the oscillating link;
When the swing link is about to rotate to one side with respect to the output shaft, the swing link is fixed to the output shaft, and the swing link is about to rotate to the other side with respect to the output shaft. A one-way rotation prevention mechanism that idles the swing link with respect to the output shaft,
An adjusting drive source for transmitting a driving force to the turning radius adjusting mechanism;
An oil pump that is driven according to the driving force of the driving source for traveling and discharges lubricating oil;
The turning radius adjusting mechanism is arranged coaxially with the input shaft, the pinion shaft to which the driving force of the adjusting drive source is transmitted, the pinion shaft is inserted at a position eccentric from the center, and the input shaft rotates. A cam part that rotates integrally with the input shaft in a state of being eccentric with respect to the central axis, and a receiving hole through which the cam part is inserted at a position that is eccentric from the center, and is eccentric with respect to the cam part And a rotatable rotating part,
External teeth are provided on the outer peripheral surface of the pinion shaft,
Inner teeth that mesh with the outer teeth are provided on the inner peripheral surface of the receiving hole of the rotating portion,
The rotation radius of the rotation part about the rotation center axis of the input shaft is such that when the pinion shaft is rotated relative to the cam part, the rotation part passes through the inner teeth and the outer teeth. Changes by rotating relative to the cam portion,
The connecting rod is connected to the turning radius adjusting mechanism by fitting the one end portion to the rotating portion via a connecting rod bearing,
A continuously variable transmission in which a gear ratio is changed by changing the turning radius of the rotating part,
A first oil passage formed on the rotation center axis of the input shaft inside the pinion shaft, and supplied with the lubricating oil from one end of the pinion shaft by the oil pump;
A second oil passage formed so as to communicate between an inner peripheral surface and an outer peripheral surface of the pinion shaft, and supplying the lubricating oil supplied via the first oil passage to the outer peripheral surface side of the pinion shaft;
A third oil passage formed to communicate the inner peripheral surface and the outer peripheral surface of the receiving hole, and supplying the lubricating oil supplied via the second oil passage to the connecting rod bearing;
A discharge oil passage for discharging a part of the lubricating oil supplied through the second oil passage to the outside of the lever crank mechanism;
The cam portion has a flange portion extending in a radial direction so as to cover an edge portion of the receiving hole,
The discharge port of the discharge oil passage is formed by the edge portion of the receiving hole and the flange portion of the cam portion,
The continuously variable transmission, wherein the flow rate of the lubricating oil discharged from the discharging oil passage changes according to a relative phase between the rotating part and the cam part. The continuously variable transmission according to claim 1,
Mounted on the vehicle,
The discharge oil passage is configured such that the flow rate of the discharged lubricant oil is minimized by a relative phase between the rotating portion and the cam portion when the traveling speed of the vehicle reaches a maximum speed. A continuously variable transmission. The continuously variable transmission according to claim 1 or 2,
The edge portion of the receiving hole is formed with a rotating portion side hole portion through which the inner peripheral surface of the receiving hole communicates with the outside of the rotating portion, and the lubricating oil is discharged.
The continuously variable transmission according to claim 1, wherein the flange portion of the cam portion is formed such that an area covering the rotating portion side hole portion can be changed in accordance with a relative phase between the rotating portion and the cam portion. The continuously variable transmission according to any one of claims 1 to 3,
The edge portion of the receiving hole of the rotating portion is formed with a rotating portion side hole portion through which the inner peripheral surface of the receiving hole communicates with the outside of the rotating portion, and the lubricating oil is discharged.
The flange part of the cam part is formed so as to cover the rotating part side hole part,
A cam portion side hole communicating with the rotating portion side hole is formed in the flange portion of the cam portion,
The continuously variable transmission, wherein an area where the rotating part side hole part and the cam part side hole part communicate with each other changes according to a relative phase between the rotating part and the cam part.