JP6141757B2 - Continuously variable transmission - Google Patents

Description

The present invention relates to a four-bar linkage-continuously variable transmission provided with a shaft receiving rotatably supporting the shaft.

  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 is rotatable about the rotation center axis of the input shaft, and a rotating radius adjusting mechanism that can adjust the rotating radius of the rotating portion; , A swing link provided with a swing end and pivotally supported by the output shaft, one end rotatably connected to the rotating portion of the turning radius adjusting mechanism, and the other end swinged And a connecting rod connected to the rocking end of the link.

  Between the swing link and the output shaft, when the swing link tries to rotate to one side around the output shaft, the swing link is fixed to the output shaft and tries to rotate to the other side. A one-way clutch is provided as a one-way rotation preventing mechanism that idles the swing link with respect to the output 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 turning radius adjusting mechanism is also kept 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 rotational center axis of the input shaft changes, and the rotational radius of the rotational radius adjusting mechanism 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 respective turning radius adjusting mechanisms allow the respective oscillating links to transmit torque to the output shaft in order so that the output shaft can be smoothly rotated.

  In addition, a connecting rod bearing is usually arranged between the rotating part of the turning radius adjusting mechanism and the connecting rod fitted around the rotating part.

JP 2012-1048 A

  In the continuously variable transmission configured as described above, the rotating portion of the turning radius adjusting mechanism rotates while being eccentric from the rotation center axis of the input shaft. In the continuously variable transmission configured as described above, when the swing link tries to rotate to one side, the driving force is transmitted to the output shaft, and when it tries to rotate to the other side, the driving force is applied to the output shaft. Do not communicate.

  Therefore, the direction and magnitude of the load applied to the rotating part and the connecting rod fitted on the rotating part during the rotation of the rotating part vary according to the rotational phase of the rotating part.

  As a result, there is a possibility that noise, vibration, and rattling may occur in the bearing when the rotating portion and the connecting rod itself are arranged, or when the bearing is disposed between them, due to the change in the load.

The present invention has been made in view of the above, the noise direction and magnitude of a load rotatably supported by the member is applied in the rotating due to changes, vibration, CVT that can suppress rattling The purpose is to provide.

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 travel 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 adjustment mechanism that is provided with a rotating portion that is rotatable about the rotation center axis of the shaft, and the rotating radius of the rotating portion can be adjusted, and a swing end portion that is swingably supported by the output shaft. And a connecting rod having one end rotatably connected to the rotating part of the turning radius adjusting mechanism and the other end connected to the swinging end of the swinging link. When the lever crank mechanism that converts the rotational motion into the swing motion of the swing link and the swing link is about to rotate to one side, the swing link is fixed to the output shaft and the swing link is about to rotate to the other side. Unidirectional rotation blocking machine that idles the swing link with respect to the output shaft When, a continuously variable transmission that includes a connecting rod bearing disposed between the rotary portion and the connecting rod, the connecting rod bearing is more between an outer ring, an inner ring, the outer ring and its inner ring A ball-shaped rolling element arranged and a cage that holds the rolling element, and the outer ring has an abutting portion that is inclined on the inner peripheral surface so as to decrease in diameter as it moves away from the bearing center in the bearing central axis direction. The inner ring has an abutting portion that is inclined so as to increase in diameter as the distance from the bearing center in the axial direction of the bearing center increases on the outer peripheral surface, the retainer has elasticity, and includes a plurality of rolling elements. The at least one rolling element is biased from one side in the bearing center axis direction, and the other side of the rolling element in the bearing center axis direction is brought into contact with the abutting portions of the outer ring and the inner ring.

As described above, in the bearing of the continuously variable transmission according to the present invention, the outer ring has the abutting portion that inclines so as to decrease in diameter as it moves away from the bearing center in the bearing central axis direction. Further, the inner ring has an abutting portion that inclines so as to increase in diameter as the inner ring moves away from the bearing center in the bearing center axis direction. The cage urges the ball-shaped rolling element from one side of the bearing central axis by its elasticity. As a result, the other side of the rolling element always comes into contact with the contact portion between the outer ring and the inner ring regardless of the gap (clearance) between the outer ring and the inner ring.

Therefore, in the bearing of the continuously variable transmission according to the present invention, even if the clearance between the outer ring and the inner ring changes, no clearance is generated between the outer ring or the inner ring and the rolling element, and the outer ring or the inner ring and the rolling element. Does not collide with each other and no impact occurs, so that noise, vibration, and rattling caused by the impact do not occur.
By the way, the continuously variable transmission of the present invention is a four-bar linkage mechanism type continuously variable transmission having a lever crank mechanism, and the rotating portion of the rotation radius adjusting mechanism rotates in a state of being eccentric from the rotation center axis of the input shaft. To do. In this continuously variable transmission, the swing link transmits a driving force to the output shaft when attempting to rotate to one side, and does not transmit the driving force to the output shaft when attempting to rotate to the other side.
Therefore, the direction and magnitude of the load applied to the rotating part and the connecting rod fitted on the rotating part during the rotation of the rotating part vary according to the rotational phase of the rotating part.
However, in the continuously variable transmission according to the present invention, since the above-described bearing is used as a connecting rod bearing disposed between the rotating portion to which such a load is applied and the connecting rod, the load applied when the rotating portion rotates. Even if the direction and size change, the noise, vibration, and backlash can be suppressed.

In the continuously variable transmission according to the present invention, the outer ring is formed with a raceway groove having contact portions on one side and the other side in the bearing central axis direction on the inner peripheral surface, and the inner ring is formed on the outer peripheral surface with a bearing. A raceway groove having a contact portion is formed on one side and the other side in the central axis direction, and the cage biases the first rolling body from the one side in the bearing central axis direction among the plurality of rolling elements. Then, the other side of the first rolling element in the bearing central axial direction is brought into contact with the contact part on the other side in the bearing central axial direction of the raceway grooves of the outer ring and the inner ring, and the second rolling element out of the plurality of rolling elements. The moving body is urged from the other side in the bearing center axis direction, and one side of the second rolling element in the bearing center axis direction is brought into contact with the one side in the bearing center axis direction of the outer and inner ring raceway grooves. It is preferable to make it contact | abut.

  Thus, if the first rolling element is brought into contact with one side of the raceway grooves of the outer ring and the inner ring, and the second rolling element is brought into contact with the other side of the raceway grooves of the outer ring and the inner ring, The forces applied to the outer ring and inner ring from the two rolling elements are opposite to each other in the bearing center axis direction, and relative movement between the outer ring and the inner ring in the bearing center axis direction can be suppressed. It becomes more difficult to collide with a moving body, and it becomes easier to further suppress noise, vibration, and rattling.

The continuously variable transmission according to the present invention further includes a plurality of first rolling elements and a plurality of second rolling elements, and the cage includes the first rolling element and the second rolling element as a bearing center axis. It is preferable to hold alternately in the circumferential direction.

  If the first rolling element and the second rolling element are held in this manner, one load in the bearing center axis direction applied to the outer ring and the inner ring from the rolling element and a load in the opposite direction are applied to the rolling element. Since it is less likely to be biased in the circumferential direction of the bearing regardless of the phase, noise, vibration, and rattling can be further suppressed.

Further, the continuously variable transmission according to the present invention includes at least three first rolling elements and at least three second rolling elements, and the cage has the first rolling element in the circumferential direction of the bearing center axis line, etc. It is preferable that the second rolling elements are held at regular intervals in the circumferential direction of the bearing center axis while being held at intervals.

  In this way, if the first rolling element and the second rolling element are provided three by three and are kept at equal intervals in the circumferential direction of the bearing central axis, the balance is improved and noise, vibration, and backlash are further improved. It becomes easy to suppress.

In the continuously variable transmission of the present invention, the cage has a plurality of pockets for holding the first rolling element or the second rolling element, and holds the first rolling element among the plurality of pockets. The pocket is formed at a position eccentric to the other side in the bearing center axis direction than the center in the bearing center axis direction of the cage, and the pocket for holding the second rolling element among the plurality of pockets is the bearing center of the cage You may comprise so that it may form in the position eccentrically located to the one side of the bearing center axial direction rather than the center of an axial direction.

1 is a partial cross-sectional view showing an embodiment of a continuously variable transmission including a bearing according to the present invention. The side view which shows the lever crank mechanism of the continuously variable transmission of FIG. FIG. 3 is an explanatory diagram 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 the maximum rotation radius, 3B is the rotation radius, 3C is the rotation radius is small, and 3D is The case where the turning radius is “0” is shown. FIG. 4 is an explanatory diagram showing a relationship between a swing range of an output side fulcrum with respect to a change in a rotation radius of an input side fulcrum of the lever crank mechanism of the continuously variable transmission of FIG. 1, wherein 4A is the maximum swing range, and 4B is a swing. The range is medium, 4C indicates a small swing range, and 4D indicates a case where the swing range is “0”. FIG. 5A is a graph showing a change in the direction of a load with respect to a rotation phase of a rotating portion of the continuously variable transmission of FIG. 1, FIG. 5A is a high gear ratio when there is no load, and FIG. 5C shows a load state at a high gear ratio, and FIG. 5D shows a load state at a low gear ratio. The graph which shows the change of the magnitude | size of the load with respect to the rotation phase of the rotation part of the continuously variable transmission of FIG. FIG. 2 is a cross-sectional view of a rotating part, a connecting rod, and a part of a connecting rod bearing of the continuously variable transmission shown in FIG. 1 as viewed from the input part side in the bearing central axis direction, where 8A indicates a no-load state and 8B indicates a load state. FIG. 8 is a cross-sectional view of the continuously variable transmission of FIG. 1 as seen from the direction intersecting the bearing central axis of the rolling elements and the cage of the connecting rod bearing of the continuously variable transmission of FIG. 1B, the peripheral part of the second rolling element in the unloaded state, 8C the peripheral part of the first rolling element in the loaded state, and 8D the peripheral part of the second rolling element in the loaded state Indicates. FIG. 2 is a developed view of a part of the rolling elements and the cage of the connecting rod bearing of the continuously variable transmission shown in FIG. 1 as viewed from the radially inner side of the bearing, where 8A indicates a no-load state and 8B indicates a load state.

  Embodiments of a continuously variable transmission including a bearing according to the present invention will be described below 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).

  With reference to FIGS. 1-6, the continuously variable transmission 1 of this 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 rotational power to drive 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 transmitted with driving force from an actuator 14 (adjusting drive source) which is a sub drive source for the pinion shaft 7. 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.

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

  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 spaced from one end wall 21a fixed to the engine ENG, the other end wall 21b disposed to face the one end wall 21a, the lever crank mechanism 20 and the one-way clutch 17. And is formed by a peripheral wall portion 21c that 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 supporting the input shaft and an opening for supporting the output shaft 3 are formed in the one end wall portion 21a and the other end wall portion 21b. Is fitted.

  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, when the swing link 18 is swung by being pushed and pulled by the connecting rod 15, the swing link 18 is pushed in the pushing direction side. Alternatively, when rotating in one of the tension direction sides, the swing link 18 is fixed to the output shaft 3 and the output shaft 3 rotates, and when the swing link 18 rotates in the other direction, the swing link 18 It idles with respect 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 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 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 infinite (∞).

  4 shows 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. FIG.

  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), and FIG. 4D shows the eccentric amount R1 which is “0” in FIG. 3D. The case (when the gear ratio h is infinite (∞)) is shown.

  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 connecting point between the connecting rod 15 and the swinging end portion 18a, that is, the center P4 of the connecting pin 19. 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, the connecting rod bearing 16 of the continuously variable transmission 1 according to the present embodiment will be described in detail with reference to FIGS. 2 and 6 to 9.

  As shown in FIG. 2, in the lever crank mechanism 20 of the continuously variable transmission 1 of the present embodiment, the rotating disk 6 of the turning radius adjusting mechanism 4 and the swinging end portion 18 a of the swinging link 18 are connected by a connecting rod 15. It is connected. The connecting rod 15 converts the rotational motion of the rotary disk 6 of the rotational radius adjusting mechanism 4 into the swing motion of the swing end 18 a of the swing link 18.

  A one-way clutch 17 is disposed between the swing link 18 and the output shaft 3. Therefore, when the one-way clutch 17 tries to rotate the swing link 18 to one side around the rotation center axis P5 of the output shaft 3, the swing link 18 transmits driving force to the output shaft 3, and when rotating to the other side, No driving force is transmitted to the output shaft 3.

  Thus, in the continuously variable transmission 1 of the present embodiment, the output from the swing link 18 connected to the rotary disk 6 via the connecting rod 15 according to the rotational phase of the rotary disk 6 of the turning radius adjusting mechanism 4. The state where the driving force is transmitted to the shaft 3 is switched between the state where the driving force is not transmitted and the state where the driving force is not transmitted.

  As a result of the experiment, noise, vibration, and rattling between the rotating disk 6 of the turning radius adjusting mechanism 4 and the input side annular portion 15a of the connecting rod 15 are relatively less likely to occur in the state where the driving force is transmitted, It was found that it is relatively easy to occur when the driving force is not transmitted.

  As shown in the graphs of FIGS. 5 and 6, the load applied to the connecting rod 15 from the rotary disk 6 of the turning radius adjusting mechanism 4 and the swing end 18 a of the swing link 18 transmits the driving force. This is because the state in which the driving force is not transmitted is smaller than the state in which the connecting rod 15 is present, and thus the connecting rod 15 is likely to move relative to the rotating disk 6.

  FIG. 5 is a graph showing changes in the direction of the load applied to the connecting rod 15 (X direction and Y direction in FIG. 2) with respect to the rotational phase of the rotating disk 6 of the turning radius adjusting mechanism 4.

  FIG. 5A is a graph in a no-load state where the transmission ratio h is relatively high (underdrive (UD)) and the connecting rod 15 does not transmit the driving force even if the connecting link 15 pushes the swing link 18 in one direction. FIG. 5B is a graph in a no-load state in which the transmission ratio h is relatively low (top drive (TD)) and the connecting rod 15 does not transmit the driving force even if the connecting link 15 pushes the swing link 18 in one direction. .

  FIG. 5C is a graph in a load state in which the driving force is transmitted when the connecting rod 15 pushes the swing link 18 in one direction with the gear ratio h being relatively high (underdrive (UD)). . FIG. 5D is a graph in a load state in which the driving force is transmitted when the connecting rod 15 pushes the swing link 18 in one direction with the gear ratio h being relatively low (top drive (TD)). .

  FIG. 6 is a graph showing changes in the magnitude of the load applied to the connecting rod 15 with respect to the rotational phase of the rotating disk 6 of the turning radius adjusting mechanism 4.

  By the way, in the continuously variable transmission 1 of the present embodiment, as shown in FIG. 7, a plurality of connecting rod bearings 16 are disposed between the outer ring 22, the inner ring 23, and the outer ring 22 and the inner ring 23. A ball-shaped rolling element comprising a first rolling element 24a and a plurality of second rolling elements 24b, and a bearing 25 that holds the first rolling element 24a and the second rolling element 24b. Is used.

  For this reason, in the connecting rod bearing 16, the direction and magnitude of the load applied when the rotating member 6 rotates, that is, the load applied to the outer ring 22 from the connecting rod 15 or the rotating disk 6 is changed. When a load is applied from the inner ring 23 to the inner ring 23, the gap (clearance) between the outer ring 22 and the inner ring 23 is reduced, and the first and second rolling elements 24a and 24b collide with the outer ring 22 or the inner ring 23. An impact may occur.

  Specifically, as shown in the graph of FIG. 6, an outer ring 22 press-fitted into the connecting rod 15 and an inner ring 23 into which the rotary disc 6 is press-fitted in accordance with a change in the load applied to the connecting rod 15 or the rotating disc 6. The clearance also changes. Then, the first rolling element 24a and the second rolling element 24b and the outer ring 22 or the inner ring 23 collide with each other to generate an impact, which may cause noise, vibration, and rattling.

  Therefore, in the connecting rod bearing 16 of the present embodiment, as shown in FIG. 8, the outer ring has an abutting portion that is inclined so as to decrease in diameter as the distance from the bearing center in the axial direction of the bearing center on the inner circumferential surface of the outer ring 22. A side raceway groove 22a is formed. The outer side in the bearing radial direction of the first rolling element 24a or the second rolling element 24b comes into contact with this contact portion.

  Similarly, as shown in FIG. 8, an inner ring side raceway groove 23 a is formed on the outer peripheral surface of the inner ring 23. The inner ring side raceway groove 23 a has a contact portion that is inclined so as to increase in diameter as the distance from the bearing center in the bearing central axis direction increases. The inner side in the bearing radial direction of the first rolling element 24a or the second rolling element 24b comes into contact with the contact portion.

  That is, in the connecting rod bearing 16 of the present embodiment, the outer ring 22, the inner ring 23, the first rolling element 24a, and the second rolling element 24b constitute a so-called groove ball bearing.

  Further, in the connecting rod bearing 16 of the present embodiment, as shown in FIGS. 8A and 8C, the cage 25 moves the first rolling element 24a to one side in the bearing central axis direction (the right side in the drawing of FIG. 8). The other side of the first rolling element 24a in the axial direction of the bearing center (the left side in FIG. 8) is brought into contact with the outer ring side raceway groove 22a of the outer ring 22 and the inner ring side raceway groove 23a of the inner ring 23. Touching.

  Similarly, as shown in FIGS. 8B and 8D, the cage 25 urges the second rolling element 24b from the other side in the bearing central axis direction (the left side in the drawing of FIG. 8), and the second One side of the rolling element 24b in the bearing central axial direction (the right side in the drawing of FIG. 8) is brought into contact with the outer ring side raceway groove 22a of the outer ring 22 and the inner ring side raceway groove 23a of the inner ring 23.

  Specifically, as illustrated in FIG. 9, the retainer 25 is formed of an elastic member, and includes a plurality of first pocket portions 25a that hold the first rolling element 24a, and a second rolling element 24b. Has a plurality of second pocket portions 25b.

  As shown in FIG. 9A, the first pocket portion 25a has a center (in FIG. 9A) in the bearing central axis direction of the cage 25 in a state where no load is applied to the outer ring 22 or the inner ring 23 (the state shown in FIG. 9A). It is formed at a position that is more eccentric than the one-dot chain line) on the other side in the bearing central axis direction (the lower side in FIG. 9A).

  As a result, the first rolling element 24a held in the first pocket portion 25a can be applied to the outer ring side raceway groove 22a of the outer ring 22 and the inner ring side raceway of the inner ring 23 even when no load is applied (the state shown in FIG. 8A). The state is in contact with the groove 23a.

  On the other hand, as shown in FIG. 9A, the second pocket portion 25b has a center (in FIG. 9A) in the bearing center axis direction of the retainer 25 in a state where no load is applied to the outer ring 22 or the inner ring 23 (the state shown in FIG. 9A). It is formed at a position that is more eccentric than one-dot chain line) on one side in the bearing central axis direction (upper side in FIG. 9A).

  As a result, the second rolling element 24b held in the second pocket portion 25b can be used for the outer ring side raceway groove 22a of the outer ring 22 and the inner ring side track of the inner ring 23 even when no load is applied (the state shown in FIG. 8B). The state is in contact with the groove 23a.

  In the connecting rod bearing 16 of the present embodiment configured as described above, when the direction and magnitude of the load applied to the outer ring 22 or the inner ring 23 changes, and the clearance between the outer ring 22 and the inner ring 23 becomes narrower ( 8A is changed from the state of FIG. 8A to the state of FIG. 8C), the load applied from the contact portion of the outer ring 22 and the inner ring 23 to the other side of the bearing central axis of the first rolling element 24a (the left side in FIG. 8). Will increase.

  At this time, since the load applied via the first rolling element 24a increases, the cage 25 is deformed by elasticity (changes from the state of FIG. 9A to the state of FIG. 9B), and the first rolling element 24a Then, it moves to one side of the bearing center axis direction (the right side in FIG. 8).

  On the other hand, when the direction and magnitude of the load applied to the outer ring 22 or the inner ring 23 is changed and the clearance between the outer ring 22 and the inner ring 23 is increased (when the state is changed from the state of FIG. 8B to the state of FIG. 8A). The load applied from the contact portion of the outer ring 22 and the inner ring 23 to the other side (the left side in FIG. 8) of the bearing center axis of the second rolling element 24b is reduced.

  At this time, since the load applied via the second rolling element 24b is reduced, the cage 25 is restored by elasticity (changed from the state of FIG. 9A to the state of FIG. 9B), and the second rolling element 24b is Then, it moves to the other side in the bearing center axis direction (left side in the drawing of FIG. 8).

  Therefore, the other side of the first rolling element 24 a is always brought into contact with the contact portion between the outer ring 22 and the inner ring 23 by the cage 25 regardless of the clearance between the outer ring 22 and the inner ring 23.

  Further, since the second rolling element 24b and the second pocket portion 25b are merely reversed in operation in the bearing central axis direction with respect to the first rolling element 24a and the first pocket portion 2a, Regardless of the clearance between the outer ring 22 and the inner ring 23, one side of the second rolling element 24 b is always brought into contact with the contact portion between the outer ring 22 and the inner ring 23.

  Therefore, according to the connecting rod bearing 16 of this embodiment, even if the clearance between the outer ring 22 and the inner ring 23 changes, the outer ring 22 or the inner ring 23 and the first rolling element 24a or the second rolling element 24 There is no clearance between the outer ring 22 and the inner ring 23 and the first rolling element 24a or the second rolling element 24b collides with each other so that no impact is generated. No rattling occurs.

  Further, in the connecting rod bearing 16 of the present embodiment configured as described above, the force applied to the outer ring 22 and the inner ring 23 from the first rolling element 24a and the second rolling element 24b is opposed in the bearing central axis direction. It has become.

  Therefore, the relative movement of the outer ring 22 and the inner ring 23 in the bearing center axis direction is suppressed, and one of the outer ring 22 or the inner ring 23 moves greatly and collides with the first rolling element 24a or the second rolling element 24b. As a result, there is no impact and no noise, vibration, or rattling is caused by the impact.

  In the connecting rod bearing 16 of the present embodiment, as shown in FIG. 7, the cage 25 has a plurality of first rolling elements 24 a and a plurality of second rolling elements 24 b in the circumferential direction of the bearing center axis. Hold alternately.

  Further, as shown in FIG. 2, the connecting rod bearing 16 of the present embodiment has a large number of first rolling elements 24a and second rolling elements 24b arranged around the entire circumference. Further, as shown in FIG. 9, the first rolling elements 24a are held at equal intervals in the circumferential direction of the bearing central axis, and the second rolling elements 24b are also held at equal intervals in the circumferential direction of the bearing central axis. ing.

  Therefore, the load applied from the first rolling element 24a to the outer ring 22 and the load applied from the second rolling element 24b to the inner ring 23 are not biased in the circumferential direction of the connecting rod bearing 16, and the balance is good. Therefore, noise, vibration, and rattle are less likely to occur.

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

  For example, in the above embodiment, a groove ball bearing is used as the connecting rod bearing 16 that is the bearing of the present invention. However, the bearing of the present invention is not necessarily a groove ball bearing, and the surface formed on the outer ring among the surfaces that contact the other side of the rolling element biased from one side of the bearing center axis is the center of the bearing. As long as it is separated from the bearing in the axial direction of the bearing, the surface is inclined so that the diameter is reduced, and the surface formed on the inner ring is inclined so that the diameter is increased as it is separated from the bearing center in the axial direction of the bearing. Specifically, for example, a step portion including an inclined surface instead of the raceway groove may be formed on the inner peripheral surface of the outer ring and the outer peripheral surface of the inner ring, and the inclined surface may be used as the contact portion.

  Moreover, in the said embodiment, the rolling element is comprised by the 1st rolling element 24a urged | biased by the outer ring | wheel side, and the 2nd rolling element 24b urged | biased by the inner ring | wheel side. However, the rolling element of the present invention is not necessarily constituted only by the first rolling element and the second rolling element. For example, you may make it include the rolling element which is not urged | biased in any direction of a bearing center axis line direction.

  Moreover, in the said embodiment, a rolling element consists of many 1st rolling elements 24a and many 2nd rolling elements 24b, and these are arrange | positioned alternately. However, the rolling element of the present invention does not necessarily need to be configured as such, and it only needs to include at least one first rolling element and one second rolling element.

  In the above embodiment, a cage-type cage having a first pocket portion 25a surrounding the first rolling element 24a and a second pocket portion 25b surrounding the second rolling element 24b is used as the cage 25. . However, the cage of the present invention does not necessarily need to use a squirrel cage, as long as it can hold a rolling element and be urged in the bearing central axis direction.

  Moreover, in the said embodiment, the 1st rolling element 24a and the 2nd rolling element 24b are hold | maintained using the holder | retainer 25 formed with the material which has elasticity. However, the cage of the present invention does not necessarily need to absorb the impact or bias the rolling element only by the elasticity of the cage. For example, a spring may be combined with an elastic member such as rubber to absorb an impact or bias a rolling element.

  In the above embodiment, the bearing of the present invention is used as the connecting rod bearing 16 of the continuously variable transmission 1 of the four-bar linkage mechanism type using the lever crank mechanism. However, the bearing of the present invention is not necessarily used only for a connecting rod bearing of a continuously variable transmission of a four-bar linkage mechanism type using a lever crank mechanism. If the bearing of the present invention is used for a bearing in which the rotation center axis of the supporting member is decentered from the bearing center axis, vibration, noise, and backlash generated in the bearing can be suppressed. Specifically, for example, it can be used as a bearing that supports a crankshaft of an engine.

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, 6 ... Rotating disk (rotating part) ), 6a ... receiving hole, 6b ... internal teeth, 7 ... pinion shaft, 7a ... pinion, 7b ... pinion bearing, 8 ... differential mechanism, 14a ... rotating shaft, 9 ... sun gear, 10 ... first ring gear, 11 ... first 2 ring gears, 12 ... stepped pinion, 12a ... large diameter part, 12b ... small diameter part, 13 ... carrier, 14 ... actuator (adjusting drive source (sub drive source)), 15 ... connecting rod, 15a ... input side annular part , 15b ... output side annular part, 16 ... connecting rod bearing, 17 ... one-way clutch (one-way rotation prevention mechanism), 18 ... swing link, 18a ... swing end, 18b ... projecting piece, 18c ... insertion hole, 19 ... Connection pin 20 ... lever crank mechanism, 21 ... transmission case, 21a ... one end wall, 21b ... other end wall, 21c ... peripheral wall, 22 ... outer ring, 22a ... outer ring side raceway groove, 23 ... inner ring, 23a ... inner ring side Track groove, 24a ... first rolling element, 24b ... second rolling element, 25 ... cage, 25a ... first pocket part, 25b ... second pocket part, 50 ... insertion hole, ENG ... engine (driving drive) Source (main drive source)), h: transmission ratio, P1: rotational axis of the input shaft, P2: center of the cam disk 5, P3: center of the rotating disk 6 (input side fulcrum), P4: center of the connecting pin 19 (Output fulcrum), P5... Rotation center axis of output shaft 3, Rx... Distance between P1 and P2, Ry... Distance between P2 and P3, R1... Distance between P1 and P3 (eccentricity, center P3 of rotating disk 6 ( Rotation radius of input side fulcrum), R2 ... P4 and P5 distance (The length of the swing link 18), .theta.1 ... rotational radius adjusting mechanism 4 of the phase, .theta.2 ... swing range of the swing link 18.

Claims (5)

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 rotating part that is rotatable about the rotation center axis of the input shaft is provided and a turning radius adjusting mechanism that can adjust the turning radius of the rotating part is provided, and a swinging end is provided to swing freely on the output shaft. A supported swinging link, and a connecting rod having one end rotatably connected to the rotating part of the turning radius adjusting mechanism and the other end connected to the swinging end of the swinging link. A lever crank mechanism for converting the rotational motion of the input shaft into the swing motion of the swing link;
When the swing link is about to rotate to one side, the swing link is fixed to the output shaft, and when the swing link is about to rotate to the other side, the swing link is idle with respect to the output shaft. A one-way rotation prevention mechanism
A continuously variable transmission comprising a connecting rod bearing disposed between the rotating portion and the connecting rod;
The connecting rod bearing includes an outer ring, an inner ring, a plurality of ball-shaped rolling elements disposed between the outer ring and the inner ring, and a cage that holds the rolling element,
The outer ring has an abutting portion inclined on the inner peripheral surface so as to decrease in diameter as the distance from the bearing center in the bearing central axis direction increases.
The inner ring has an abutting portion that is inclined on the outer peripheral surface so as to increase in diameter as the distance from the bearing center in the bearing central axis direction increases.
The cage has elasticity, and urges at least one rolling element of the plurality of rolling elements from one side in the bearing central axial direction, and causes the other side of the rolling element in the bearing central axial direction to move. A continuously variable transmission which is brought into contact with the contact portions of the outer ring and the inner ring. The continuously variable transmission according to claim 1,
The outer ring is formed with a raceway groove having the contact portion on one side and the other side in the bearing central axis direction on the inner peripheral surface,
The inner ring is formed with a raceway groove having an abutting portion on one side and the other side in the bearing central axis direction on the outer peripheral surface,
The cage urges the first rolling element from the one side in the bearing center axial direction among the plurality of rolling elements, and the other side of the first rolling element in the bearing central axial direction is used as the outer ring. And the abutting portion on the other side in the bearing center axial direction of the raceway groove of the inner ring to urge the second rolling element of the plurality of rolling elements from the other side in the bearing central axis direction. Te, stepless, characterized in that one side of the bearing axis line direction of the second rolling element, is brought into contact with the contact portion of one side of the bearing axis line direction of the outer ring and the raceway groove of the inner ring Transmission . The continuously variable transmission according to claim 2,
A plurality of the first rolling elements and a plurality of the second rolling elements,
The said retainer hold | maintains the said 1st rolling element and the said 2nd rolling element alternately in the circumferential direction of a bearing center axis line, The continuously variable transmission characterized by the above -mentioned . The continuously variable transmission according to claim 2 or claim 3,
Comprising at least three first rolling elements and at least three second rolling elements;
The retainer holds the first rolling elements at equal intervals in the circumferential direction of the bearing central axis, and holds the second rolling elements at equal intervals in the circumferential direction of the bearing central axis. Continuously variable transmission . A continuously variable transmission according to any one of claims 2 to 4,
The cage has a plurality of pockets for holding the first rolling element or the second rolling element,
Of the plurality of pockets, a pocket for holding the first rolling element is formed at a position eccentric to the other side in the bearing center axis direction than the center in the bearing center axis direction of the cage,
Of the plurality of pockets, a pocket for holding the second rolling element is formed at a position eccentric to one side in the bearing center axis direction from the center in the bearing center axis direction of the cage. Continuously variable transmission .