JP2015102173A - Power transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a power transmission device capable of further suppressing deflection of a shaft.SOLUTION: A power transmission device 1 includes an input shaft 2 rotated in a case, an output shaft disposed in parallel with a rotation central axis of the input shaft 2, a one-way clutch, and a plurality of crank mechanisms #1-#6 converting a rotating motion of the input shaft 2 into an oscillating motion of an oscillation link. The input shaft 2 includes two end journal portions respectively supported by bearings 90 at both end portions, and an intermediate journal portion supporting an intermediate portion of the input shaft 2 by a bearing 91. The first to sixth lever crank mechanisms #1-#6 successively transmits driving force from the input shaft 2 to the output shaft according a rotation phase of the input shaft 2. The lever crank mechanisms #1-#6 transmitting the driving force next after the driving force is transmitted by any one of the lever mechanisms #1-#6, is disposed over the intermediate journal portion.

Description

  The present invention relates to a power transmission device of a four-bar linkage mechanism type that can be changed by adjusting a rotation radius with a rotation radius adjustment mechanism provided on a rotation center axis of an input shaft.

  Conventionally, a hollow input shaft that rotates in a case by transmitting a driving force from a main drive source such as an engine provided in a vehicle, an output shaft that is arranged in parallel with the input shaft, and rotation of the input shaft A plurality of turning radius adjusting mechanisms provided on the central axis, a plurality of swing links pivotally supported on the output shaft, and an input side annular portion rotatably fitted on the turning radius adjusting mechanism at one end There is known a four-bar linkage mechanism type power transmission device including a connecting rod having the other end connected to the swing end of the swing link (see, for example, Patent Document 1).

  The input shaft, the output shaft, the turning radius adjusting mechanism, the swing link, and the connecting rod of Patent Document 1 constitute a lever crank mechanism. Between the swing link and the output shaft, the swing link is fixed to the output shaft when trying to rotate relative to the output shaft on one side, and the output shaft is fixed when trying to rotate relative to the other side. On the other hand, a one-way clutch is provided as a one-way rotation prevention mechanism that idles the swing link.

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

  When the rotational speed of the input shaft that is rotated by the main drive source and the carrier that is rotated by the adjustment drive source is the same, the eccentricity of the center point of the rotating portion with respect to the input center axis of the input shaft is maintained, and the rotation radius The radius of the rotation locus of the adjusting mechanism is also kept constant. When the rotational speed of the input shaft rotated by the main drive source and the carrier rotated by the adjustment drive source are different, the amount of eccentricity of the center point of the rotating part with respect to the rotation center axis of the input shaft changes, and the rotation radius adjustment mechanism The radius of rotational motion also changes.

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

  In such a power transmission device, the distance between the center point of the equilateral triangle whose apex is the center axis of the three pinions and the input center axis of the input shaft, and the center point of the equilateral triangle and the center point of the rotating part Is set equal to each other, the rotation center axis of the input shaft and the center point of the rotating part can be overlapped to make the amount of eccentricity zero. When the amount of eccentricity is 0, even when 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.

JP 2012-1048 A

  In a power transmission device including an input / output inter-axis transmission mechanism, shaft deflection occurs. In order to suppress this bending as much as possible, it is conceivable to provide an intermediate journal portion that supports the intermediate portion of the shaft with a bearing.

  An object of this invention is to provide the power transmission device which can further suppress the bending of a shaft.

  In order to achieve the above object, the present invention has an input shaft that rotates within a case by transmission of a driving force of a main drive source, an output shaft that is arranged in parallel with the rotation center axis of the input shaft, and an outer ring. When the outer ring is fixed to the output shaft when the outer ring tries to rotate relative to the output shaft, and the outer ring tries to rotate relative to the output shaft relative to the other A unidirectional rotation blocking mechanism for causing the outer ring to idle with respect to the output shaft, and a plurality of input / output shaft transmission mechanisms for converting the rotational movement of the input shaft into the oscillating movement of the outer ring. One of the input shaft and the output shaft includes two end journal portions whose both ends are supported by bearings, and an intermediate journal portion which supports the middle portion of the one shaft by bearings, The input / output shaft transmission mechanism rotates the input shaft. The driving force is transmitted sequentially from the input shaft to the output shaft in accordance with the phase, and any one of the plurality of input / output shaft transmission mechanisms is driven by the input / output shaft transmission mechanism. After the transmission, the input / output shaft transmission mechanism for transmitting the driving force next is disposed across the intermediate journal portion.

  In the case of providing an intermediate journal part, if the transmission mechanism between the input and output shafts between one end journal part and the intermediate journal part transmits the driving force, the intermediate journal part is located between the one end journal part and the intermediate journal part. In this case, the shaft is bent. At this time, bending in the opposite direction occurs on the opposite side across the intermediate journal portion.

  According to the present invention, when the transmission mechanism between the input and output shafts that transmits the driving force is switched between the input shaft and the output shaft, the transmission mechanism between the input and output shafts that transmits power next straddles the intermediate journal portion. Therefore, bending in the opposite direction of the shaft is suppressed. Accordingly, as a result, the deflection of the entire shaft can be suppressed.

  Moreover, in this invention, it is preferable to comprise the bearing used by an intermediate | middle journal part larger diameter than the bearing used by an edge part journal part. It has been found that when the transmission mechanism between the input and output shafts for transmitting the power is configured to straddle the intermediate journal part to suppress the deflection of the shaft, the load applied to the intermediate journal part increases. Therefore, if the bearing used in the intermediate journal portion is configured to have a larger diameter than the bearing used in the end journal portion, it can be firmly supported even when a large load is applied.

  In the present invention, the transmission mechanism between the input and output shafts is provided eccentrically with respect to the rotation center axis of the input shaft, and is freely rotatable in a state of being eccentric to the cam portion and the cam portion rotating integrally with the input shaft. The intermediate journal portion includes an insertion portion that is inserted into the bearing, and the insertion portion includes a recess that is recessed in the axial direction of one of the shafts, and is adjacent to the intermediate journal portion. A part of the cam portion of the input / output shaft transmission mechanism is preferably located in the recess.

  When the intermediate journal portion is provided, the axial length of the power transmission device is increased accordingly. In this case, if a recess is provided in the insertion part of the intermediate journal part and a part of the cam part is disposed in the recess, it is possible to suppress an increase in the axial length of the power transmission device.

  In the present invention, six input / output shaft transmission mechanisms are provided, and the phase interval of the input / output shaft transmission mechanism is set to 120 °, 120 ° from one of the rotation center axes of the input shaft as one shaft, The intermediate journal portion can be arranged between the third and fourth input / output shaft transmission mechanisms, counting from one of the rotation center axes, by setting the angle to −60 °, 120 °, and 120 °.

  Further, according to the present invention, the transmission mechanism between the input and output shafts includes a rotation radius adjustment mechanism capable of adjusting the rotation radius, and by adjusting the rotation radius of the rotation radius adjustment mechanism, the rotation speed of the input shaft is changed and output. It can also be applied to those that can be transmitted to the shaft.

Explanatory drawing which shows embodiment of the power transmission device of this invention in a partial cross section. Explanatory drawing which shows the lever crank mechanism of this embodiment. Explanatory drawing which shows the change of the rotation radius of this embodiment. 3A shows a state where the turning radius is maximum, FIG. 3B shows a case where the turning radius is medium, FIG. 3C shows a case where the turning radius is small, and FIG. 3D shows a state where the turning radius is zero. Explanatory drawing which shows the change of the rocking | fluctuation range of an outer ring with respect to the change of the rotation radius of this embodiment. FIG. 4A shows the swing range when the turning radius is the maximum, FIG. 4B shows the inside of the turning radius, and FIG. 4C shows the swing range when the turning radius is small. Sectional drawing which expands and shows the part of the input shaft of this embodiment. Explanatory drawing which shows typically the arrangement | positioning of the phase of the cam part of this embodiment. Explanatory drawing which shows typically the power transmission of this embodiment, and the bending of a shaft. Explanatory drawing which shows the conventional power transmission and the bending of a shaft typically.

  An embodiment of the power transmission device of the present invention will be described with reference to FIGS. The power transmission device according to the present embodiment is a transmission that can change the speed ratio h (h = rotational speed of the input shaft / rotational speed of the output shaft) to infinity (∞), so that the rotational speed of the output shaft can be “0”, so-called. It is a kind of IVT (Infinity Variable Transmission).

  Referring to FIG. 1, a power transmission device 1 of a four-bar linkage mechanism type rotates about a rotation center axis P1 by transmitting a driving force from a main driving source ENG such as an engine such as an internal combustion engine or an electric motor. An output shaft 3 disposed parallel to the rotation center axis P1 and transmitting rotational power to drive wheels (not shown) of the vehicle via a differential gear (not shown), and the rotation center axis P1 And six turning radius adjusting mechanisms 4 provided on the head. A propeller shaft may be provided instead of the differential gear.

  1 and 2, each turning radius adjusting mechanism 4 includes a cam disk 5 as a cam part and a rotating disk 6 as a rotating part. The cam disks 5 have a disk shape, are eccentric from the rotation center axis P <b> 1, and are provided in each rotation radius adjustment mechanism 4 so as to form one set with respect to one rotation radius adjustment mechanism 4. . The cam disk 5 is provided with a through hole 5a penetrating in the direction of the rotation center axis P1. Further, the cam disk 5 is opened in a direction opposite to the direction decentered with respect to the rotation center axis P1, and a notch hole 5b for communicating the outer peripheral surface of the cam disk 5 with the inner peripheral surface constituting the through hole 5a. Is provided.

  Each set of cam disks 5 is arranged so as to make a round in the circumferential direction of the rotation center axis P <b> 1 with six sets of cam disks 5 with a phase difference of 60 degrees.

  The cam disk 5 is formed integrally with the cam disk 5 of the adjacent turning radius adjusting mechanism 4 to constitute an integrated cam portion 5c. The integrated cam portion 5c may be formed by integral molding, or may be integrated by welding two cam portions. A pair of cam disks 5 of each turning radius adjusting mechanism 4 are fixed by bolts (not shown). The cam disk 5 located on the most main drive source side on the rotation center axis P1 is formed integrally with the input shaft end 2a. In this way, the input shaft 2 including the cam disk 5 is configured by the input shaft end portion 2 a and the plurality of cam disks 5.

  The input shaft 2 includes an insertion hole 60 formed by connecting the through holes 5 a of the cam disk 5. Thereby, the input shaft 2 is configured in a hollow shaft shape in which one end opposite to the main drive source ENG is open and the other end is closed. The cam disk 5 located at the other end on the main drive source side is formed integrally with the input shaft end 2a. As a method of integrally forming the cam disk 5 and the input shaft end 2a, integral molding may be used, or the cam disk 5 and the input shaft end 2a may be integrated by welding. .

  Each set of cam disks 5 is rotatably fitted with a disk-shaped rotating disk 6 having a receiving hole 6a for receiving the cam disk 5 in an eccentric state.

  As shown in FIG. 2, the rotating disk 6 has a cam disk 5 center point P2 and a rotating disk 6 center point P3, a distance Ra between the rotation center axis P1 and the center point P2, and the center point P2 and the center point. It is eccentric with respect to the cam disk 5 so that the distance Rb of P3 is the same.

  The receiving hole 6 a of the rotating disk 6 is provided with internal teeth 6 b that are positioned between the pair of cam disks 5.

  In the insertion hole 60 of the camshaft 51, the pinion 70 is positioned so as to be concentric with the rotation center axis P <b> 1 and corresponding to the inner teeth 6 b of the rotary disk 6, and the pinion 70 rotates relative to the input shaft 2 having the cam disk 5. It is arranged to be free. The pinion 70 is formed integrally with the pinion shaft 72. The pinion 70 may be configured separately from the pinion shaft 72, and the pinion 70 may be connected to the pinion shaft 72 by spline coupling. In the present embodiment, the term “pinion 70” is defined as including the pinion shaft 72.

  The pinion 70 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 shaft 72 is provided with a pinion bearing 74 positioned between the adjacent pinions 70. The pinion shaft 72 supports the input shaft 2 via the pinion bearing 74. A differential mechanism 8 composed of a planetary gear mechanism or the like is connected to the pinion shaft 72. The driving force of the adjusting drive source 14 is transmitted to the pinion 70 via the differential mechanism 8.

  Since the rotating disk 6 is eccentric with respect to the cam disk 5 such that the distance Ra and the distance Rb are the same, the center point P3 of the rotating disk 6 is positioned on the same axis as the rotation center axis P1. Thus, the distance between the rotation center axis P1 and the center point P3, that is, the eccentricity R1 can be set to “0”.

  The peripheral edge of the rotary disk 6 is provided with a large-diameter input-side annular portion 15a at one end (on the input shaft 2 side), and at the other end (output shaft 3 side) at the end of the input-side annular portion 15a. An input side annular portion 15a of a connecting rod 15 having a small-diameter output side annular portion 15b is externally fitted rotatably via a connecting rod bearing 16 comprising two ball bearings arranged side by side in the axial direction. Six swing links 18 corresponding to the connecting rod 15 are provided on the output shaft 3 via a one-way clutch 17. In the present embodiment, the swing link 18 also has a function as an outer ring of the one-way clutch 17.

  The one-way clutch 17 is provided between the swing link 18 and the output shaft 3. When the swing link 18 is about to rotate relative to the output shaft 3 on one side, the swing link 18 is connected to the output shaft. 3 (fixed state), and the rocking link 18 is idled with respect to the output shaft 3 (idle state) when trying to rotate relatively to 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 protruding pieces 18b protruding so as to sandwich the output-side annular portion 15b in 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. A connecting pin 19 as a swing shaft is inserted into the insertion hole 18c and the output side annular portion 15b. Thereby, the connecting rod 15 and the swing link 18 are connected.

  In the present embodiment, the oscillating end 18a is disposed below the output shaft 3 so that the oscillating end 18a of the oscillating link 18 is immersed in the oil reservoir of lubricating oil collected below the case 80. Has been. As a result, the oscillating end 18a can be lubricated with the oil reservoir, and the oscillating motion of the oscillating link 18 can lift the lubricating oil in the oil reservoir and lubricate other components of the power transmission device 1. .

  In the description of the present embodiment, the gear ratio is defined as the rotational speed of the input shaft / the rotational speed of the output shaft.

  FIG. 3 shows the positional relationship between the pinion shaft 72 and the rotating disk 6 in a state where the eccentric amount R1 (rotating radius) of the rotating radius adjusting mechanism 4 is changed. FIG. 3A shows a state where the eccentric amount R1 is “maximum”, and the pinion shaft is such that the rotation center axis P1, the center point P2 of the cam disk 5, and the center point P3 of the rotation disk 6 are aligned. 72 and the rotary disk 6 are located. At this time, 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 “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 and the center point P3 of the rotating disk 6 are located concentrically. The gear ratio h at this time is infinite (∞). In the power transmission device 1 of the present embodiment, the rotational radius of the rotational radius adjusting mechanism 4 can be adjusted by changing the eccentric amount R1 by the rotational radius adjusting mechanism 4.

  FIG. 4 shows a change in the swing range of the swing link 18 when the eccentric amount R1 of the turning radius adjusting mechanism 4 is changed. 4A shows the swing range of the swing link 18 when the eccentric amount R1 is the maximum, FIG. 4B shows the swing range of the swing link 18 when the eccentric amount R1 is medium, and FIG. The swing range of the swing link 18 when the eccentric amount R1 is small is shown. It can be seen from FIG. 4 that the swing range becomes narrower as the eccentric amount R1 becomes smaller. When the eccentric amount R1 becomes “0”, the swing link 18 does not swing.

  In the present embodiment, the turning radius adjusting mechanism 4, the connecting rod 15, and the swing link 18 constitute a lever crank mechanism 20 (four-bar linkage mechanism). Then, the lever crank mechanism 20 converts the rotational motion of the input shaft 2 into the swing motion of the swing link 18. The power transmission device 1 of this embodiment includes a total of six lever crank mechanisms 20. When the input shaft 2 is rotated and the pinion shaft 72 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. Accordingly, the swing link 18 swings between the input shaft 2 and the output shaft 3 by alternately pushing the swing end 18a toward the output shaft 3 or pulling it toward the input shaft 2 side.

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

  In addition, the power transmission device of the present embodiment includes a control unit (not shown) that controls the adjustment drive source 14. The control unit is an electronic unit composed of a CPU, a memory, and the like, and the control program stored in the memory is executed by the CPU, thereby controlling the adjustment drive source 14 and the amount of eccentricity of the turning radius adjustment mechanism 4. It functions to regulate R1.

  The power transmission device 1 of this embodiment includes a case 80 that rotatably supports the input shaft 2. As shown in FIG. 5, the case 80 is positioned at the center portion of the input shaft 2 and is provided with a partition wall 80 a. The input shaft 2 is pivotally supported by bearings 90 at both ends thereof. Both ends supported by the bearing 90 correspond to the end journal portion of the input shaft of the present invention. In FIG. 1, the partition wall 80a and the intermediate journal bearing 91 are omitted.

  Moreover, the input shaft 2 is supported by the partition wall 80a via the bearing 91 in the center part. A portion of the central portion of the input shaft 2 supported by the case 80 via the bearing 91 and the partition wall 80a corresponds to the intermediate journal portion of the input shaft of the present invention.

  FIG. 6 schematically shows the arrangement of the lever crank mechanism 20 as the input / output shaft transmission mechanism of the present embodiment. The lever crank mechanism 20 of the present embodiment is arranged in order from the adjustment drive source 14 side, the first lever crank mechanism # 1, the second lever crank mechanism # 2, the third lever crank mechanism # 3, the fourth lever crank mechanism # 4, The fifth lever crank mechanism # 5 and the sixth lever crank mechanism # 6 are used.

  As shown in FIG. 6, the phase difference of the cam disk 5 of the lever crank mechanism 20 as the transmission mechanism between the input and output shafts is determined in the order of the first lever crank mechanism # 1 to the sixth lever crank mechanism # 6. The phase difference between the cam disk 5 of the mechanism # 1 and the second lever crank mechanism # 2 is set to 120 °, and the phase difference between the cam disk 5 of the second lever crank mechanism # 2 and the third lever crank mechanism # 3 is set to 120 °. The

  Further, the phase difference between the cam disks 5 of the third lever crank mechanism # 3 and the fourth lever crank mechanism # 4 is −60 °, and the positions of the cam disks 5 of the fourth lever crank mechanism # 4 and the fifth lever crank mechanism # 5 are the same. The phase difference is set to 120 °, and the phase difference between the cam disks 5 of the fifth lever crank mechanism # 5 and the sixth lever crank mechanism # 6 is set to 120 °.

  By setting the phase difference between the cam disks 5 in this way, the lever crank mechanism 20 serving as the input / output shaft transmission mechanism for transmitting power is, for example, the intermediate journal portion after the first lever crank mechanism # 1. Next to the sixth lever crank mechanism # 6 and the sixth lever crank mechanism # 6, the intermediate journal portion is placed next to the second lever crank mechanism # 2 and the second lever crank mechanism # 2 across the intermediate journal portion. Next to the fourth lever crank mechanism # 4 and the fourth lever crank mechanism # 4, the intermediate journal portion is next to the third lever crank mechanism # 3 and the third lever crank mechanism # 3. Next to the fifth lever crank mechanism # 5 and the fifth lever crank mechanism # 5, the first lever crank mechanism # 1 straddles the intermediate journal part and the lever that always transmits power across the intermediate journal part. Link mechanism 20 is switched.

  Accordingly, for example, when the deflection of the input shaft 2 occurs on the left side downward from the intermediate journal portion of FIG. 7, the deflection occurs on the opposite upper side on the right side of FIG. 7 across the intermediate journal portion. Can be suppressed by the lever crank mechanism 20 that transmits power next time.

  Therefore, according to the power transmission device 1 of this embodiment, the bending of the input shaft 2 can be suppressed.

  Further, in FIG. 7, when the lever crank mechanism 20 that transmits power so as to straddle the intermediate journal portion is switched as indicated by an arrow at the top of the drawing, the load applied to the bearing 91 at the intermediate journal portion increases. For this reason, in the power transmission device 1 of the present embodiment, the bearing 91 is configured to have a larger diameter than the bearing 90 provided in the end journal portion. Thereby, a load can be appropriately received by the bearing 91 of the intermediate journal part.

  Further, when the intermediate journal portion is provided, the input shaft 2 becomes longer in the axial direction by that amount. Therefore, in the present embodiment, a pair of recesses 101 that are recessed in the axial direction of the input shaft 2 are provided in the insertion portion 100 of the input shaft 2 that is inserted into the bearing 91 in the intermediate journal portion. A part of the cam disk 5 is positioned in the recess 101. Thereby, the increase in the axial length of the input shaft 2 by providing an intermediate journal part can be suppressed.

  FIG. 8 shows a case where the lever crank mechanism 20 for transmitting power from the first lever crank mechanism # 1 to the sixth lever crank mechanism # 6 is switched in order from the first lever crank mechanism # 1 without straddling the intermediate journal portion in the conventional power transmission device. The bending of the input shaft 2 is shown. It can be seen that the deflection of the input shaft 2 increases.

  In the present embodiment, the input shaft 2 has been described as the shaft on which the intermediate journal portion is provided, but the output shaft 3 may be used.

  In the present embodiment, the description has been given of the case where only one intermediate journal part is provided, but there may be a plurality of intermediate journal parts.

  Moreover, in this embodiment, what crossed the intermediate journal part was demonstrated in all when the lever crank mechanism 20 which transmits motive power switches. However, a part when the lever crank mechanism 20 for transmitting power is switched (specifically, the number of the lever crank mechanisms 20 continuous without straddling the intermediate journal part is more than twice the number of the intermediate journal parts, Even if it is configured to straddle the intermediate journal part in a number that exceeds the number of intermediate journal parts by more than twice the number of intermediate journal parts in one cycle), it is inferior to the present embodiment but more than the conventional power transmission device The bending of the shaft can be suppressed.

  In the present embodiment, the input shaft end portion 2 a and the plurality of cam disks 5 constitute the input shaft 2, and the input shaft 2 is formed by connecting the through holes 5 a of the cam disk 5. Explained what provided.

  However, the input shaft of the present invention is not limited to this. For example, as a component part of the input shaft, a hollow input shaft core portion having an insertion hole whose one end is open and the other end is closed is provided. An input having a plurality of cam disks is formed by forming a through hole larger than that of the present embodiment so that the input shaft core portion can be inserted into the disk, and by connecting each cam disk to the outer peripheral surface of the input shaft core portion by spline. An axis may be configured.

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

  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 for example, from an oscillation link as an outer ring to an output shaft. Alternatively, a two-way clutch configured to be able to switch the rotation direction with respect to the output shaft of the swing link capable of transmitting torque to the shaft may be used.

DESCRIPTION OF SYMBOLS 1 Power transmission device 2 Input shaft 2a Input shaft end 2b Input shaft bearing 3 Output shaft 3a Output shaft bearing 4 Turning radius adjustment mechanism 5 Cam disk (cam portion)
5a Through-hole 5b Notch hole 5c Integrated cam part 6 Rotating disk (rotating part)
6a Receiving hole (inner circumference)
6b Internal gear 8 Differential mechanism (Planetary gear mechanism)
12 Stepped pinion 14 Adjustment drive source (motor)
15 Connecting rod 15a Input side annular portion 15b Output side annular portion 16 Connecting rod bearing 17 One-way clutch 18 Swing link (outer ring)
18a Swing end 18b Projection piece 18c Insertion hole 19 Connection pin 20 Lever crank mechanism (four-bar linkage mechanism)
60 Insertion hole 70 Pinion 72 Pinion shaft 74 Pinion bearing 80 Case 80a Partition wall 90 Bearing of end journal portion 91 Bearing of intermediate journal portion 100 Insertion portion 101 Recess P1 Rotation center axis P2 Center point P3 of cam disc P3 Center of rotation disc Distance Ra between points Ra P1 and P2 Distance Rb between P2 and P3 Eccentricity (distance between P1 and P3)

Claims (5)

An input shaft that rotates in the case by transmission of the driving force of the main drive source,
An output shaft disposed parallel to the rotation center axis of the input shaft;
An outer ring is provided, the outer ring is fixed to the output shaft when the outer ring is about to rotate relative to the output shaft, and the outer ring is rotated relative to the output shaft. A one-way rotation prevention mechanism that idles the outer ring with respect to the output shaft when attempting to;
A power transmission device comprising a plurality of input / output shaft transmission mechanisms for converting the rotational motion of the input shaft into the swing motion of the outer ring,
One shaft of the input shaft and the output shaft includes two end journal portions whose both ends are supported by bearings, and an intermediate journal portion which supports the middle portion of the one shaft by bearings,
The input / output shaft transmission mechanism sequentially transmits a driving force from the input shaft to the output shaft according to the rotational phase of the input shaft.
After the input / output shaft transmission mechanism of any one of the plurality of input / output shaft transmission mechanisms transmits the driving force, the input / output shaft transmission mechanism that transmits the driving force next is the intermediate journal. A power transmission device characterized by being disposed across the section. The power transmission device according to claim 1,
The power transmission device according to claim 1, wherein a bearing used in the intermediate journal portion has a larger diameter than a bearing used in the end journal portion. The power transmission device according to claim 1 or 2,
The transmission mechanism between the input and output shafts is provided eccentrically with respect to the rotation center axis of the input shaft, and is provided rotatably with a cam portion that rotates integrally with the input shaft and with the cam portion being eccentric. With a rotating part,
The intermediate journal part includes an insertion part inserted into the bearing,
The insertion portion includes a recess that is recessed toward the axial direction of the one shaft,
A part of the cam portion of the input / output shaft transmission mechanism adjacent to the intermediate journal portion is located in the recess. The power transmission device according to any one of claims 1 to 3,
Six input / output shaft transmission mechanisms are provided,
The phase interval of the input / output shaft transmission mechanism is set to 120 °, 120 °, −60 °, 120 °, 120 ° from one of the rotation center axes of the input shaft as the one shaft,
The intermediate journal portion is disposed between the third and fourth input / output shaft transmission mechanisms, counting from one of the rotation center axes. The power transmission device according to any one of claims 1 to 4,
The input / output shaft transmission mechanism includes a rotation radius adjustment mechanism capable of adjusting a rotation radius;
The power transmission device, wherein the rotational speed of the input shaft is changed and transmitted to the output shaft by adjusting the rotational radius of the rotational radius adjusting mechanism.