JP5694859B2 - Four-bar link type continuously variable transmission - Google Patents

Description

  The present invention relates to a continuously variable transmission using a “lever / crank mechanism” which is a typical structure of a four-bar link.

  Conventionally, a hollow input shaft to which driving force from a drive source such as an engine provided in a vehicle is transmitted, an output shaft arranged in parallel with the input shaft, and a plurality of eccentric mechanisms provided on the input shaft, There are a plurality of swing links pivotally supported on the output shaft, a large-diameter annular portion that is rotatably fitted to the eccentric mechanism at one end, and the other end of the swing link There is known a four-bar link type continuously variable transmission including a connecting rod connected to a swing end (see, for example, Patent Document 1).

  In Patent Document 1, each eccentric mechanism is composed of a fixed disk provided eccentrically on the input shaft, and a swinging disk provided eccentrically on the fixed disk and 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 is maintained. When the rotational speeds of the input shaft and the pinion shaft are made different, the eccentric amount of the eccentric mechanism is changed, and the transmission gear ratio is changed.

  When the eccentric mechanism 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 swings. . 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.

  The eccentric direction of the fixed disk of each eccentric mechanism is set so as to make a round around the input shaft with different phases. Therefore, the swinging link sequentially transmits the torque to the output shaft by the connecting rod fitted to each eccentric mechanism, so that the output shaft can be smoothly rotated.

JP-T-2005-502543

  As a lubrication structure of a transmission, an oil hole that connects an oil passage and an oil passage to an outer peripheral surface is formed in an input shaft, an output shaft, and the like, and the lubricating oil is discharged from the oil hole, so that a gear meshing portion, etc. Lubricating structures for lubricating oil are known.

  However, the inventors of the present invention have the largest load per unit area of the connecting portion between the connecting rod and the swing link in the above-described four-bar link type continuously variable transmission, and the heat resistance, durability, wear resistance From the viewpoint of safety, it has been found that appropriate lubrication and cooling of the connecting portion is necessary, and that the connecting portion may not be properly lubricated by a conventionally used lubrication method.

  In view of the above, an object of the present invention is to provide a four-bar link type continuously variable transmission that can supply lubricating oil more appropriately to the connecting portion between the connecting rod and the swing link than in the past.

  [1] In order to achieve the above object, the present invention provides a hollow input shaft to which a driving force from a vehicle drive source is transmitted, an output shaft arranged in parallel with the input shaft, and a bias to the input shaft. A plurality of eccentric mechanisms having a fixed disk provided in the center, a swing disk provided eccentrically with respect to the fixed disk, and a plurality of swing links pivotally supported by the output shaft; The swing link is fixed to the output shaft and is relatively rotated to the other side when attempting to rotate relative to the output shaft on one side. A one-way rotation prevention mechanism that idles the swinging link with respect to the output shaft when attempting to, a large-diameter annular portion that is rotatably fitted to the eccentric mechanism at one end, and the other Connected to the end of the swing link connected to the swing end of the swing link A rod and a pinion shaft inserted into the input shaft, and the input shaft is formed with a notch at a location facing the eccentric direction of the fixed disk, and the pinion shaft is exposed from the notch. The swing disk is provided with a receiving hole for receiving the input shaft and the fixed disk, and an inner tooth is formed on an inner peripheral surface of the swing disk that forms the receiving hole. The eccentric amount of the eccentric mechanism is maintained by meshing with the pinion shaft exposed from the notch hole of the shaft and rotating the input shaft and the pinion shaft at the same speed, and the rotation of the input shaft and the pinion shaft. A four-bar link continuously variable transmission that controls the transmission ratio by changing the amount of eccentricity of the eccentric mechanism by varying the speed, wherein the swing end portion of the swing link has a front end A guide groove is provided above the output shaft, and a guide groove is provided on the upper surface of the other end portion for guiding at least a part of the lubricating oil adhering to the upper surface to a connecting portion between the connecting rod and the swinging end portion, Of the swing range of the swing link, the guide groove is the swing end of the swing link, with the position closest to the input shaft as the inner dead center and the position farthest from the input shaft as the outer dead center. When the portion is located at the outer dead center, the bottom surface is provided with an inclined surface formed so as to incline horizontally or downward toward the outer dead center side.

  According to such a configuration, at least a part of the lubricating oil adhering to the upper surface of the other end of the connecting rod is guided to the connecting portion between the connecting rod and the swinging end by the guide groove. The connecting portion with the rocking end is lubricated and cooled more appropriately than in the past.

Also, in the present invention, the guide groove is the swing link swinging position with the position closest to the input shaft as the inner dead center and the position farthest from the input shaft as the outer dead center within the swing range of the swing link. When the moving end portion is located at the external dead center, an inclined surface formed so as to incline downward toward the horizontal or external dead center side is provided as a bottom surface .

  If the bottom surface of the guide groove is an inclined surface, at least a part of the lubricating oil adhering to the upper surface of the other end of the connecting rod is supplied to the connecting portion between the connecting rod and the swing link through the inclined surface. The Further, even when the bottom surface of the guide groove is horizontal, when the swing end portion of the swing link is located at the external dead center, the swing end portion moves toward the inner dead center side thereafter. The lubricating oil adhering to the horizontal bottom surface of the guide groove tends to stay at the current position due to the inertial force, so that the lubricating oil moves relatively to the other end side with respect to the connecting rod. As a result, it is supplied to the connecting portion between the connecting rod and the swinging end.

  Therefore, according to the four-bar link type continuously variable transmission of the present invention, it is possible to appropriately supply the lubricating oil to the connecting portion between the connecting rod and the swinging end as compared with the conventional one.

[ 2,3 ] In the present invention, if the inclined surface is the first inclined surface, the bottom surface of the guide groove is inclined downwardly more than the first inclined surface toward the outer dead center side in addition to the first inclined surface. It is preferable to provide the 2nd slope formed in this.

  When the oscillating end of the oscillating link is moving toward the outer dead center, the lubricating oil in the guide groove is moved relatively to the inner dead center with respect to the connecting rod by the inertial force. If a second inclined surface is formed on the bottom surface of the guide groove so as to be greatly downwardly inclined toward the outer dead center side with respect to the first inclined surface, the connecting portion between the connecting rod and the swinging end portion, or lubrication on the first inclined surface. The second inclined surface can prevent the oil from moving relative to the connecting rod toward the inner dead center side.

[ 4 ] In the present invention, a small-diameter annular portion is provided at the other end of the connecting rod, and a pair of projecting pieces projecting so as to sandwich the small-diameter annular portion in the axial direction are provided at the oscillating end of the oscillating link. The connecting rod and the swing link can be connected by providing a through hole corresponding to the inner diameter of the small-diameter annular portion in the pair of projecting pieces and inserting a connecting pin into the through-hole and the small-diameter annular portion. .

  At this time, if a cutout portion that is notched so as to widen the exposed area of the connecting pin between the small-diameter annular portion and the protruding piece is formed at the upper ends of the pair of protruding pieces, the lubricating oil dripped from above is cutout. To the connecting pin. As a result, according to the four-bar link continuously variable transmission of the present invention, the lubricating oil can be supplied more appropriately to the connecting portion between the connecting rod and the swinging end.

Sectional drawing which shows embodiment of the continuously variable transmission to which the lubricating oil supply structure of this invention is applied. Explanatory drawing which shows the eccentric mechanism of this embodiment, a connecting rod, and a rocking | fluctuation link from an axial direction. Explanatory drawing explaining the change of the eccentric amount of the eccentric mechanism of this embodiment. It is explanatory drawing which shows the relationship between the change of the eccentric amount of the eccentric mechanism of this embodiment, and rocking | swiveling angle (theta) 2 of the rocking | fluctuation motion of a rocking | fluctuation link, (a) is the maximum eccentricity, (b) is eccentricity. (C) shows the swing angle of the swing motion of the swing link when the amount of eccentricity is small. The graph which shows the change of angular velocity (omega) 2 of a rocking | fluctuation link with respect to the change of the eccentric amount of the eccentric mechanism of this embodiment. In the continuously variable transmission of this embodiment, the graph which shows the state in which an output shaft is rotated by six four-bar linkage mechanisms which respectively made the phase different 60 degree | times. The perspective view which shows the other edge part of the connecting rod of this embodiment. (A) is a perspective view which shows the connection part of the connecting rod and swing link of this embodiment, (b) is a perspective view which shows the swing end part of the swing link of this embodiment.

  Hereinafter, an embodiment of a continuously variable transmission to which a lubricating oil supply structure of the present invention is applied will be described. The continuously variable transmission according to the present embodiment is a transmission capable of setting the speed ratio i (i = rotational speed of the input shaft / rotational speed of the output shaft) to infinity (∞) and the rotational speed of the output shaft to “0”. It is a kind of so-called Infinity Variable Transmission (IVT).

  1 and 2, the continuously variable transmission 1 of the present embodiment receives an input central axis P1 by receiving rotational power from a vehicle drive source such as an internal combustion engine (not shown) or an electric motor. A hollow input shaft 2 that rotates about the center, and an output shaft 3 that is arranged in parallel to the input shaft 2 and that transmits rotational power to drive wheels (not shown) of the vehicle via a differential gear, a propeller shaft, etc. (not shown) And six eccentric mechanisms 4 provided on the input shaft 2.

  Each eccentric mechanism 4 includes a fixed disk 5 and a swing disk 6. The fixed disks 5 have a disk shape and are provided in pairs on the input shaft 2 so as to be eccentric from the input center axis P1 and rotate integrally with the input shaft 2. Each set of fixed disks 5 is arranged so as to make a round in the circumferential direction of the input shaft 2 with six sets of fixed disks 5 with a phase difference of 60 degrees. Further, a disc-shaped rocking disc 6 having a receiving hole 6a for receiving the fixed disc 5 is eccentrically fitted to each set of fixed discs 5 so as to be rotatable.

  The oscillating disk 6 has a center point of the fixed disk 5 as P2, a center point of the oscillating disk 6 as P3, a distance Ra between the input center axis P1 and the center point P2, and a distance Rb between the center point P2 and the center point P3. Are eccentric with respect to the fixed disk 5 so as to be the same.

  The receiving hole 6 a of the swing disk 6 is provided with an internal tooth 6 b positioned between the pair of fixed disks 5. The input shaft 2 is formed between a pair of fixed disks 5 and is formed with a notch hole 2 a that communicates the inner peripheral surface and the outer peripheral surface at a location facing the eccentric direction of the fixed disk 5.

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

  A differential mechanism 8 is connected to the pinion shaft 7. The differential mechanism 8 is configured by a planetary gear mechanism, and includes a sun gear 9, a first ring gear 10 connected to the input shaft 2, a second ring gear 11 connected to the pinion shaft 7, a sun gear 9 and A carrier 13 is provided that supports a stepped pinion 12 including a large-diameter portion 12a that meshes with the first ring gear 10 and a small-diameter portion 12b that meshes with the second ring gear 11 so as to rotate and revolve freely.

  The sun gear 9 is connected to a rotation shaft 14a of a drive source 14 composed of an electric motor for the pinion shaft 7. When the rotational speed of the drive source 14 is the same as the rotational speed of the input shaft 2, the sun gear 9 and the first ring gear 10 rotate at the same speed, and the sun gear 9, the first ring gear 10, and the second ring gear 11 are rotated. In addition, the four elements of the carrier 13 are in a locked state where relative rotation is impossible, 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 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 (first The number of rotations of the carrier 13 is (j · Nr1 + Ns) / (j + 1) where j is the number of teeth of one ring gear 10 / the number of teeth of the sun gear 9). The gear ratio between the sun gear 9 and the second ring gear 11 ((number of teeth of the second ring gear 11 / number of teeth of the sun gear 9) × (number of teeth of the large diameter portion 12a of the stepped pinion 12 / tooth of the small diameter portion 12b) (Number)) is k, the rotation speed of the second ring gear 11 is {j (k + 1) Nr1 + (k−j) Ns} / {k (j + 1)}.

  When the rotational speed of the input shaft 2 to which the fixed disk 5 is fixed and the rotational speed of the pinion shaft 7 are the same, the oscillating disk 6 rotates together with the fixed disk 5. When there is a difference between the rotational speed of the input shaft 2 and the rotational speed of the pinion shaft 7, the oscillating disk 6 rotates the periphery of the fixed disk 5 around the center point P <b> 2 of the fixed disk 5.

  As shown in FIG. 2, the oscillating disk 6 is eccentric with respect to the fixed disk 5 so that the distance Ra and the distance Rb are the same, so that the center point P3 of the oscillating disk 6 is set to the input center axis P1. The distance between the input center axis P1 and the center point P3, that is, the eccentric amount R1 can be set to “0”.

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

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

  FIG. 3 shows the positional relationship between the pinion shaft 7 and the oscillating disk 6 in a state where the eccentric amount R1 of the eccentric mechanism 4 is changed. FIG. 3A shows a state in which the eccentricity R1 is set to “maximum”, and the input center axis P1, the center point P2 of the fixed disk 5, and the center point P3 of the swing disk 6 are aligned. In addition, the pinion shaft 7 and the swing disk 6 are located. At this time, the gear ratio i is minimized.

  FIG. 3B shows a state in which the eccentric amount R1 is set to “medium” which is smaller than that in FIG. 3A, and FIG. 3C illustrates that the eccentric amount R1 is smaller than that in FIG. Is shown. The gear ratio i is “medium” which is larger than the gear ratio i in FIG. 3A in FIG. 3B, and “large” which is larger than the gear ratio i in FIG. 3B in FIG. Become. FIG. 3D shows a state where the amount of eccentricity R1 is “0”, and the input center axis P1 and the center point P3 of the oscillating disk 6 are located concentrically. The gear ratio i at this time is infinite (∞).

  As shown in FIG. 2, the eccentric mechanism 4, the connecting rod 15, and the swing link 18 of the present embodiment constitute a four-bar linkage mechanism 20. The continuously variable transmission 1 of this embodiment includes a total of six four-bar linkage mechanisms 20. When the input shaft 2 is rotated and the pinion shaft 7 is rotated at the same speed as the input shaft 2 when the eccentric amount R1 is not “0”, each connecting rod 15 changes its phase by 60 degrees, and the eccentric amount R1. On the basis of this, it is repeatedly swung between the input shaft 2 and the output shaft 3 by alternately pushing to the output shaft 3 side or pulling to the input shaft 2 side.

  Since the small-diameter annular portion 15b of the connecting rod 15 is connected to the swing link 18 provided on the output shaft 3 via the one-way clutch 17, the swing link 18 is pushed and pulled by the connecting rod 15 to swing. Then, the output shaft 3 rotates only when the swing link 18 rotates in either the pushing direction side or the pulling direction side, and the output shaft 3 rotates when the swing link 18 rotates in the other direction. Thus, the force of the swing motion of the swing link 18 is not transmitted to the swing link 18, and the swing link 18 is idled. Since each eccentric mechanism 4 is arranged with a phase changed every 60 degrees, the output shaft 3 is rotated in turn by each eccentric mechanism 4.

  4A shows the case where the eccentric amount R1 is “maximum” in FIG. 3A (when the gear ratio i is the minimum), and FIG. 4B shows the case where the eccentric amount R1 is “ 4 (c) shows the case where the eccentric amount R1 is “small” in FIG. 3 (c) (when the gear ratio i is large). The swing range θ2 of the swing link 18 with respect to the rotational movement of the eccentric mechanism 4 is shown. As is clear from FIG. 4, as the amount of eccentricity R1 decreases, the swing range θ2 of the swing link 18 decreases. When the eccentric amount R1 is “0”, the swing link 18 does not swing. In the present embodiment, the position closest to the input shaft 2 in the swing range θ2 of the swing end 18a of the swing link 18 is the internal dead center, and the position farthest from the input shaft 2 is the external dead center. .

  FIG. 5 shows the relationship of the change in the angular velocity ω2 with the change in the eccentric amount R1 of the eccentric mechanism 4 with the rotation angle θ of the eccentric mechanism 4 of the continuously variable transmission 1 as the horizontal axis and the angular velocity ω2 of the swing link 11 as the vertical axis. Indicates. As is apparent from FIG. 5, it can be seen that the angular velocity ω2 of the swing link 11 increases as the eccentric amount R1 increases (the transmission ratio i decreases).

  FIG. 6 shows the rotation angle θ of the eccentric mechanism 4 when the six eccentric mechanisms 4 whose phases are different by 60 degrees are rotated (when the input shaft 2 and the pinion shaft 7 are rotated at the same speed). The angular velocity ω2 of each swing link 18 is shown. From FIG. 6, it can be seen that the output shaft 3 is smoothly rotated by the six four-bar linkage mechanisms 20.

  As shown in FIG. 7, a pair of guide grooves 21 and 21 are provided on the upper surface of the other end of each connecting rod 15 along the side edge. Each guide groove 21 has a bottom surface formed by combining two types of slopes, a first slope 21a and a second slope 21b. The bottom surface of each guide groove 21 extends from one end of the connecting rod 15 toward the other end of the second inclined surface 21b, the first inclined surface 21a, the second inclined surface 21b, the first inclined surface 21a, and the second inclined surface 21b. It is provided in order.

  The first inclined surface 21a is formed so as to incline downward toward the horizontal or external dead center side when the swing end portion 18a of the swing link 18 is located at the external dead center. The second inclined surface 21b is formed so as to be inclined more downward than the first inclined surface 21a toward the outer dead center when the swinging end portion 18a of the swing link 18 is located at the outer dead center.

  When a part of the lubricating oil scattered in the transmission case or a part of the lubricating oil dripped from the upper surface of the transmission case adheres to the upper surface of the connecting rod 15, the adhered lubricating oil causes the operation of the connecting rod 15. As a result, the upper surface is moved. Then, the lubricating oil that has entered the guide groove 21 tends to stay on the absolute shaft by the inertial force when the connecting rod 15 is pulled toward the input shaft 2, and as a result, with respect to the connecting rod 15. It will move to the other end side. Since the first inclined surface 21a is inclined horizontally or downward at the external dead center, the lubricating oil on the first inclined surface 21a can be appropriately guided to the connecting pin 19.

  Conversely, when the connecting rod 15 is pressed toward the output shaft 3, the lubricating oil on the first inclined surface 21a tends to move toward the input shaft 2 with respect to the connecting rod 15, but the second inclined surface 21b is Since the inclination angle is set to be steeper than the one inclined surface 21a, this can be suppressed.

  Therefore, according to the guide groove 21 of the present embodiment, the lubricating oil adhering to the second inclined surface 21b located closest to the large-diameter annular portion 15a is guided to the adjacent first inclined surface 21a and from the external dead center. When moving to the inner dead center side, the lubricating oil on the first inclined surface 21a passes through the second inclined surface 21b on the small diameter annular portion 15b side and is guided to the first inclined surface 21a on the small diameter annular portion 15b side. When moving from the point to the outer dead center side, the second inclined surface 21b prevents the lubricant on the first inclined surface 21a from moving to the large-diameter annular portion 21a side, and again moves from the outer dead point to the inner dead center side. When this is done, it passes through the second inclined surface 21b located closest to the small-diameter annular portion 15b and is guided to the outer peripheral surface of the connecting pin 19.

  The lubricating oil guided to the outer peripheral surface of the connecting pin 19 has a force to return to the guide groove 21 when moving again from the inner dead center to the outer dead center side, but is located closest to the small-diameter annular portion 15b. Returning into the guide groove 21 is prevented by the second inclined surface 21b.

  As shown in FIGS. 8A and 8B, the upper end of the protruding piece 18b of the swing link 18 is cut so as to widen the exposed area of the connecting pin 19 between the small-diameter annular portion 15b and the protruding piece 18b. A notched portion 18d is provided. More lubricating oil splashing in the transmission case can be attached to the connecting pin 19 through the notch 18d, and more lubricating oil is supplied between the connecting pin 19 and the small-diameter annular portion 15b. Can do. Further, the upper edge of the notch 18d is chamfered and inclined, and the lubricating oil adhering to the upper end of the swinging end 18a can be guided into the notch 18d by this chamfering.

  In addition, although the guide groove 21 of this embodiment is provided so that the side edge of the connecting rod 15 may be followed, the guide groove of this invention may be formed in the upper surface center of the connecting rod 15 not only in this. . In this case, a communication port that communicates with the inner peripheral surface of the small-diameter annular portion may be formed at the end of the guide groove on the output shaft side.

  Moreover, although the guide groove 21 of this embodiment is provided with the two 1st slope 21a and the 3rd 2 slope 21b, the guide groove of this invention is not restricted to this. For example, you may comprise the bottom face of a guide groove only with one 1st slope.

  In the present embodiment, the one-way clutch 17 is used as the one-way rotation prevention mechanism. However, the one-way rotation prevention mechanism of the present invention is not limited to this, and torque is applied from the swing link 18 to the output shaft 3. May be configured by a two-way clutch (two-way clutch) configured to be able to switch the rotation direction of the swing link 18 capable of transmitting the rotation relative to the output shaft 3.

DESCRIPTION OF SYMBOLS 1 ... Continuously variable transmission, 2 ... Input shaft, 2a ... Notch hole, 3 ... Output shaft, 4 ... Eccentric mechanism, 5 ... Fixed disk, 6 ... Swing disk, 6a ... Receiving hole, 6b ... Internal tooth, 7 ... Pinion shaft, 7a ... external teeth, 8 ... differential mechanism (planetary gear mechanism), 9 ... sun gear, 10 ... first ring gear, 11 ... second ring gear, 12 ... stepped pinion, 12a ... large diameter part, 12b DESCRIPTION OF SYMBOLS ... Small diameter part, 13 ... Carrier, 14 ... Drive source (electric motor), 14a ... Rotating shaft, 15 ... Connecting rod, 15a ... Large diameter annular part, 15b ... Small diameter annular part, 16 ... Roller bearing, 17 ... One-way clutch ( Unidirectional rotation prevention mechanism), 18 ... swing link, 18a ... swing end, 18b ... projecting piece, 18c ... through hole, 18d ... notch, 19 ... connecting pin, 20 ... four-bar linkage mechanism, 21 ... guide Groove, 21a ... first slope, 21b ... second slope P1 ... input center axis, P2 ... fixed disc center point, P3 ... oscillating disc center point, Ra ... P1 and P2 distance, Rb ... P2 and P3 distance, R1 ... eccentricity (distance between P1 and P3) , Θ2: Swing range

Claims (4)

A hollow input shaft to which a driving force from a driving source of the vehicle is transmitted;
An output shaft arranged parallel to the input shaft;
A plurality of eccentric mechanisms including a fixed disk provided eccentrically with respect to the input shaft, and a swinging disk provided eccentrically with respect to the fixed disk and rotatably provided;
A plurality of swing links pivotally supported by the output shaft;
The swing link is provided between the swing link and the output shaft, and the swing link is fixed to the output shaft when attempting to rotate relative to the output shaft and relative rotation to the other side. A one-way rotation prevention mechanism that idles the swing link with respect to the output shaft when
A connecting rod having a large-diameter annular portion that is rotatably fitted to the eccentric mechanism at one end, and the other end connected to the swing end of the swing link;
A pinion shaft inserted into the input shaft,
In the input shaft, 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 rocking disk that forms the receiving hole,
The inner teeth mesh with the pinion shaft exposed from the notch hole of the input shaft,
The eccentric amount of the eccentric mechanism is maintained by rotating the input shaft and the pinion shaft at the same speed, and the eccentric amount of the eccentric mechanism is changed by changing the rotational speeds of the input shaft and the pinion shaft. And a four-bar link continuously variable transmission that controls the gear ratio,
The swing end of the swing link is disposed above the output shaft,
A guide groove is provided on the upper surface of the other end portion to guide at least a part of the lubricating oil adhering to the upper surface to a connecting portion between the connecting rod and the swinging end portion,
Of the swinging range of the swing link, a position closest to the input shaft is an internal dead center, and a position farthest from the input shaft is an external dead center.
The guide groove includes, as a bottom surface, an inclined surface formed so as to incline horizontally or downward toward the outer dead center when the swing end of the swing link is located at the outer dead center. A four-bar link continuously variable transmission characterized by The four-bar link continuously variable transmission according to claim 1 ,
When the inclined surface is the first inclined surface,
In addition to the first slope, the bottom surface includes a second slope formed so as to incline below the first slope toward the outer dead center side, and has a second slope. Step transmission. A hollow input shaft to which a driving force from a driving source of the vehicle is transmitted;
An output shaft arranged parallel to the input shaft;
A plurality of eccentric mechanisms including a fixed disk provided eccentrically with respect to the input shaft, and a swinging disk provided eccentrically with respect to the fixed disk and rotatably provided;
A plurality of swing links pivotally supported by the output shaft;
The swing link is provided between the swing link and the output shaft, and the swing link is fixed to the output shaft when attempting to rotate relative to the output shaft and relative rotation to the other side. A one-way rotation prevention mechanism that idles the swing link with respect to the output shaft when
A connecting rod having a large-diameter annular portion that is rotatably fitted to the eccentric mechanism at one end, and the other end connected to the swing end of the swing link;
A pinion shaft inserted into the input shaft,
In the input shaft, 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 rocking disk that forms the receiving hole,
The inner teeth mesh with the pinion shaft exposed from the notch hole of the input shaft,
The eccentric amount of the eccentric mechanism is maintained by rotating the input shaft and the pinion shaft at the same speed, and the eccentric amount of the eccentric mechanism is changed by changing the rotational speeds of the input shaft and the pinion shaft. And a four-bar link continuously variable transmission that controls the gear ratio,
The swing end of the swing link is disposed above the output shaft,
A guide groove is provided on the upper surface of the other end portion to guide at least a part of the lubricating oil adhering to the upper surface to a connecting portion between the connecting rod and the swinging end portion,
The guide groove includes a first slope and a second slope as a bottom surface thereof,
Of the swing range of the swing link, a position closest to the input shaft is an internal dead center, and a position farthest from the input shaft is an external dead center.
The second inclined surface is inclined so as to incline downward toward the outer dead center when the swinging end portion is located at the outer dead center, and toward the outer dead center. A four-bar link type continuously variable transmission, characterized in that the four-link type continuously variable transmission is formed so as to incline downward. The four-bar link type continuously variable transmission according to any one of claims 1 to 3 ,
A small-diameter annular portion is provided at the other end of the connecting rod,
The swing end portion of the swing link is provided with a pair of projecting pieces projecting so as to sandwich the small-diameter annular portion in the axial direction,
In the pair of projecting pieces, through holes corresponding to the inner diameter of the small-diameter annular portion are formed,
By inserting a connecting pin into the through hole and the small-diameter annular portion, the connecting rod and the swing link are connected,
The four-bar link is characterized in that a cutout portion is formed at the upper end of the pair of projecting pieces so as to widen the exposed area of the connecting pin between the small-diameter annular portion and the projecting piece. Type continuously variable transmission.