CN106183783A - Stepless speed changing mechanism - Google Patents

Abstract

The present invention provides a continuously variable transmission mechanism capable of suppressing a reduction in the dimensional accuracy of the inner diameter of a through hole through which a crank pin passes due to an opening of an eccentric disc. The 1st and 2nd crankshaft journals (16p-16v, 17p-17v) are provided respectively as projected portions obtained by projecting the 1st and 2nd crankshaft journals (16p-16v, 17p-17v) in the axial direction (N1) Located within the outline (N2) of the first and second crank pins (16p-16v, 17p-17v) connected to the first and second crank journals (16p-16v, 17p-17v). The axial width (L1) of the eccentric disc (14) is smaller than the axial length (L2) of the first and second crankshaft journals.

Description

CVT

technical field

The present invention relates to a crank-type continuously variable transmission mechanism that converts the eccentric rotation of an eccentric disc that rotates together with an input shaft into reciprocating oscillations of an input member of a one-way clutch via a connecting member, and converts the reciprocating oscillations of the input member through the one-way clutch. In particular, the present invention relates to a continuously variable transmission mechanism capable of continuously changing an eccentric amount of a continuously variable transmission, which is converted into unidirectional intermittent rotation of an output shaft.

Background technique

Patent Document 1 describes a continuously variable transmission that converts rotation of an input shaft connected to an engine into reciprocating motion of a connecting rod, and further converts reciprocating motion of the connecting rod into rotational motion of an output shaft through a one-way clutch.

Patent Document 1: Japanese Patent No. 5142234

The crank-type continuously variable transmission mechanism of Patent Document 1 has a crankshaft member having: a plurality of crankshaft journals having a common central axis; The axis is eccentric, and an eccentric disc is rotatably fitted to each of the plurality of crank pins. Since each crank pin is eccentric in a different direction, it is not possible to insert the eccentric disk into the crankshaft component from the axial direction and assemble it. Each eccentric disk is constructed by butting two semicircular parts divided in the radial direction and fastening them with bolts. . If the eccentric disc is formed into a butt joint structure of two semicircular parts, when a large torque or load acts on the continuously variable transmission mechanism, the two semicircular parts will act on the direction of mutual separation and open. , which may adversely affect the dimensional accuracy of the inner diameter of the through-hole through which the crankpin passes. In addition, there is a concern that production costs increase, such as an increase in the number of parts and an increase in assembly man-hours.

Contents of the invention

An object of the present invention is to provide a continuously variable transmission mechanism that can integrally mold an eccentric disk rotatably fitted to a crankpin, and that can be assembled to each crankpin from the axial direction of the crankshaft member, and can prevent the opening of the eccentric disk from As a result, the dimensional accuracy of the inner diameter of the through hole through which the crank pin penetrates decreases.

In order to achieve the above object, the invention according to claim 1 is a continuously variable transmission mechanism (for example, a continuously variable transmission mechanism BD in an embodiment described later) comprising: an input shaft (for example, a The input shaft 151 in the embodiment), the input shaft receives the rotational power generated from the power source and rotates around the input central axis (for example, the input central axis O1 in the embodiment described later); a plurality of eccentric discs (for example, the rear The eccentric disk 14 in the embodiment described above), the plurality of eccentric disks have a first fulcrum (for example, the first fulcrum O3 in the embodiment described later) at their respective centers, and each first fulcrum is on the input central axis The surroundings are arranged at equal intervals in the circumferential direction, and the eccentricity of each first fulcrum relative to the input central axis (for example, the eccentricity r in the embodiment described later) can be changed. Rotating together with the input shaft around the input center axis while maintaining the eccentricity, and the first through hole and the second through hole extending parallel to the input center axis are respectively formed on the plurality of eccentric disks. holes (for example, the first through hole 14a and the second through hole 14b in the embodiment described later); the first crankshaft member (for example, the first crankshaft member 16 in the embodiment described later), the first crankshaft member It has a plurality of first crank pins (for example, first crank pins 16c to 16h in an embodiment described later) and a plurality of first crank journals (for example, first crank journals 16p to 16p in an embodiment described later). 16v), the plurality of first crank pins rotatably pass through the first through-holes formed in the plurality of eccentric disks and are connected to each other, and the plurality of first crank pins respectively There is a center axis (for example, a center axis 16b in an embodiment described later) at a position offset by an equal distance from the center axis of the first crankpin (for example, a center axis 16k in an embodiment described later); component (for example, the second crankshaft member 17 in the embodiment described later), the second crankshaft member has a plurality of second crankpins (for example, the second crankpins 17c to 17h in the embodiment described later) and a plurality of second crankpins (for example, second crankpins 17p to 17v in the embodiment described later), the plurality of second crankpins rotatably penetrate the plurality of eccentric discs formed on the The second through-holes are connected to each other, and the plurality of second crankpins are respectively located at positions offset by an equal distance from the central axis of each second crankpin (for example, the central axis 17k in the embodiment described later). There is a central axis at the position (for example, the central axis 17b in the embodiment described later); a one-way clutch (for example, the one-way clutch OWC in the embodiment described later), the one-way clutch has The output member (for example, the clutch inner member 121 in the embodiment described later) that rotates on the output center axis (for example, the output center axis O2 in the embodiment described later) receives power in the direction of rotation from the outside and rotates around the The input member (for example, described later) that the output center axis swings The clutch outer member 122 in the embodiment), and the engagement member (for example, the roller 123 in the embodiment described later) that makes these input members and output members mutually locked or unlocked, when the input member When the forward rotation speed exceeds the forward rotation speed of the output member, the one-way clutch transmits the rotational power input to the input member to the output member, thereby converting the swing motion of the input member into the Rotational movement of the above-mentioned output member; a plurality of connecting members (for example, the connecting member 130 in the embodiment described later), one end of each of the plurality of connecting members (for example, the ring part 131 in the embodiment described later) The first fulcrum is rotatably connected to the outer circumference of each of the eccentric disks, and the other ends of the plurality of connecting members (for example, the terminal 132 in the embodiment described later) are rotatably connected to the outer circumference of each of the eccentric disks. The second fulcrum (for example, the second fulcrum O4 in the embodiment described later) provided on the input member of the clutch at a position deviated from the output central axis, thereby applying the force from the input shaft to the The rotational motion of the eccentric disc is transmitted to the input member as the swing motion of the input member of the one-way clutch; The variable mechanism includes an actuator (for example, an actuator 180 in an embodiment described later) for causing the first crankpin and the second crankpin to move in the first and second crankpins, respectively. 2. The crankshaft journal rotates synchronously around the center to adjust the eccentricity of the first fulcrum with respect to the input center axis, thereby changing the degree of swing motion transmitted from the eccentric disc to the input member of the one-way clutch. As a result, the variable speed ratio mechanism changes the rotational power input to the input shaft when the rotational power input to the input shaft is transmitted as rotational power to the output member of the one-way clutch via the eccentric plate and the connecting member. gear ratio, and since the eccentricity can be set to zero, the gear ratio can be set to infinity, wherein the outer diameters of the plurality of first crankpins (for example, in the embodiments described later The outer diameters D1) are all equal or increase from one side to the other in the axial direction, and the outer diameters of the plurality of second crankpins (for example, the outer diameter D3 in the embodiment described later) are all equal or within The axial direction becomes larger from one side to the other side, and the plurality of first crank journals are each provided as a projected portion obtained by projecting the first crank journal in the axial direction (for example, as described later). The projected portion N1) in the embodiment of the first crankshaft pin is located within the contour of the first crank pin connected to the first crankshaft journal (for example, the contour N2 in the embodiment described later), and the plurality of second crankshaft shafts The journals are provided such that a projected portion obtained by projecting the second crank journal in the axial direction (for example, a projected portion N1 in the embodiment described later) is located on the said second crank journal connected to the second crank journal. Within the profile of the second crankpin (eg, profile N2 in the embodiment described later), the axial widths of the plurality of eccentric discs (eg, rear The axial width L1) in the above-described embodiment is smaller than the axial lengths of the first crank journal and the second crank journal (for example, the axial length L2 in the embodiment described later).

In addition, in the invention according to claim 2, in the invention according to claim 1, the first through-hole and the second through-hole formed in the eccentric disk do not communicate with each other.

According to the invention described in claim 1, the outer diameters of the plurality of first crank pins are all equal or become larger from one side to the other in the axial direction, and the plurality of first crank journals are respectively provided so as to oppose each other in the axial direction. The projected portion obtained by projecting the first crankshaft journal is located within the contour of the first crankpin connected to the first crankshaft journal, and the outer diameters of the plurality of second crankpins are all equal or axially from one to the other. The side becomes larger toward the other side, and a plurality of second crankshaft journals are respectively arranged so that the projected portion obtained by projecting the second crankshaft journal in the axial direction is located at the position of the second crankpin connected to the second crankshaft journal. inside the outline. In addition, since the axial width of the eccentric disk is smaller than the axial length of the first and second crankshaft journals, the eccentric disk that is integrally formed without being divided in the radial direction can be separated from the first and second crankshaft members. Insert one side toward the other side in turn for assembly. Therefore, it is possible to prevent a reduction in the dimensional accuracy of the inner diameter of the through hole through which the crank pin passes due to the opening of the eccentric disk, and to prevent a change in the amount of eccentricity, thereby suppressing the influence on the gear ratio. In addition, since the eccentric disc is integrally formed, the number of parts can be reduced.

According to the invention described in claim 2, since the first and second through-holes formed in the eccentric disk do not communicate with each other, the rigidity of the eccentric disk can be increased, and changes in the amount of eccentricity of the eccentric disk can be more reliably prevented.

Description of drawings

FIG. 1 is a cross-sectional view showing a continuously variable transmission mechanism of a reference example.

Fig. 2 is a side view of the continuously variable transmission mechanism shown in Fig. 1 .

Fig. 3 is a perspective view showing main parts of the continuously variable transmission mechanism.

Fig. 4 is a side view of each crankshaft member in the continuously variable transmission mechanism.

Fig. 5 is a side view showing two types of eccentric disks in the continuously variable transmission mechanism.

Fig. 6 is an explanatory view showing the positional relationship between each eccentric disc and each crank pin constituting the continuously variable transmission mechanism.

FIG. 7 is an action diagram showing changes in rotation angles of 60° when an eccentric disc in a continuously variable transmission mechanism rotates around an input central axis with an eccentric amount fixed.

8 is an explanatory diagram showing a state in which the eccentricity of the eccentric disk in the continuously variable transmission mechanism is changed for every 45° rotation angle of each crankshaft member.

Fig. 9 shows the positional relationship between each eccentric plate and each crank pin under each eccentric amount of the continuously variable transmission mechanism, wherein (a) is a diagram showing a state where the eccentric amount r is "zero", (b) is a diagram showing a state where the eccentricity r is "medium", and (c) is a diagram showing a state where the eccentricity r is "large".

FIG. 10 is a schematic diagram showing a four-joint link mechanism of a continuously variable transmission mechanism.

11 is an action diagram showing changes in the swing amount of the one-way clutch outer member when the eccentricity of the eccentric disc of the continuously variable transmission mechanism is different, wherein (a) is "large" showing that the eccentricity r is large (b) is a diagram showing a state where the eccentricity r is "medium" smaller than that of (a), and (c) is a diagram showing that the eccentricity r is "medium" smaller than that of (b). A picture of the state of "small".

Fig. 12 is a diagram showing the eccentricity r (gear ratio i) of the eccentric disc rotating at a constant speed with the input shaft in the continuously variable transmission mechanism, and the input in the case of changing "large", "medium" and "small". A graph of the relationship between the rotational angle θ of the shaft and the swing angular velocity ω2 of the input member of the one-way clutch.

13 is a diagram for explaining the principle of derivation of output when power is transmitted from the input side (input shaft or eccentric disk) to the output side (output member of the one-way clutch) using a plurality of connecting members in the continuously variable transmission mechanism.

Fig. 14 is a sectional view showing the continuously variable transmission mechanism of the present invention.

Fig. 15 is a perspective cross-sectional view showing a state where an eccentric disc is attached to a crankshaft member.

Fig. 16 is a perspective view illustrating the assembly of the eccentric disk to the crankshaft member.

Fig. 17 is a plan view of the crankshaft assembly and eccentric disc.

(a) of FIG. 18 is a right side view of FIG. 17 , and (b) is a cross-sectional view along line XVIII-XVIII in FIG. 17 .

19 is a perspective view of a crankshaft member and an eccentric disk assembled in a state where the eccentric amount of the eccentric disk is zero.

Label description

14: Eccentric disc;

14a: the first through hole;

14b: the second through hole;

16: 1st crankshaft component;

16b: the central axis of the first crankshaft journal;

16c～16h: 1st crankshaft pin;

16k: the central axis of each first crankpin;

16p～16v: 1st crankshaft journal;

17: The second crankshaft component;

17b: the central axis of the second crankshaft journal;

17c～17h: 2nd crankshaft pin;

17k: the central axis of each second crankpin;

17p～17v: 2nd crankshaft journal;

112: gear ratio variable mechanism;

121: clutch inner part (output part);

122: clutch outer part (input part);

123: roller (bonding part);

130: connecting parts;

131: ring part (one end);

132: end (the other end);

151: input shaft;

180: actuator;

BD': stepless speed change mechanism;

D1: Outer diameter of the first crankshaft pin;

D2: Outer diameter of the first crankshaft journal;

D3: Outer diameter of the second crankshaft pin;

D4: Outer diameter of the second crankshaft journal;

D5: Aperture diameter of the first through hole (diameter of the first through hole);

D6: Aperture diameter of the second through hole (diameter of the second through hole);

L1: the axial width of the eccentric disc;

L2: axial length of the 1st and 2nd crankshaft journals;

N1: projection part;

N2: Contour;

O1: input central axis;

O2: Output central axis;

O3: the first fulcrum;

O4: the second fulcrum;

OWC: one-way clutch;

r: eccentricity.

detailed description

First, a reference example having the same basic structure as the continuously variable transmission mechanism of the present invention will be described with reference to FIGS. 1 to 13 .

The continuously variable transmission mechanism of the reference example is a type of transmission mechanism called IVT (Infinity Variable Transmission = a transmission mechanism in which the transmission ratio is infinitely increased without using a clutch, and the output rotation can be zeroed). The continuously variable transmission mechanism BD is configured such that the transmission ratio i can be continuously changed and the maximum value of the transmission ratio can be set to infinity (∞).

As shown in FIG. 1 , the continuously variable transmission mechanism BD includes: an input shaft 151 connected to an output shaft S of a drive source such as an engine, and rotates around an input central axis O1 by receiving rotational power from the drive source; There are 6 eccentric discs 104 (hereinafter, the 6 eccentric discs are also referred to as 104A to 104F), which rotate integrally with the input shaft 151 via the first and second crankshaft members 106 and 107; The same number of connecting members 130 for connecting the input side and the output side; and the one-way clutch OWC provided on the output side.

Also as shown in Figure 2, Figure 3 and Figure 5, a plurality of eccentric discs 104 are respectively formed in a circular shape with the first fulcrum O3 as the center, and each first fulcrum O3 is located at the input center at equal intervals along the circumferential direction. It is arranged around the axis O1. In addition, the plurality of eccentric disks 104 eccentrically rotate around the input center axis O1 as the input shaft 151 rotates while maintaining the eccentric amount r. In addition, the plurality of eccentric disks 104 is configured such that the amount of eccentricity r of each first fulcrum O3 with respect to the input center axis O1 can be changed. Moreover, two through-holes 104a, 104b extending parallel to the input central axis O1 are formed in the plurality of eccentric disks 104, respectively.

As shown in FIGS. 1 to 4 , the first crankshaft member 106 has a plurality of first crankpins 106 c to 106 h rotatably penetrating through two through holes formed in the plurality of eccentric disks 104 via sliding bearings 155 . 104a, 104b in one through hole 104a, and they are connected to each other; and a plurality of first crankpins 106p, 106q, 106r, which are offset by an equal distance from the central axis 106k of each of the first crankpins 106c~106h The location has a central axis 106b.

The second crankshaft member 107 also has a plurality of second crankpins 107c to 107h, which are respectively rotatably inserted through the other through-hole 104b formed in the plurality of eccentric disks 104 through the sliding bearing 155, and they are connected to each other. and a plurality of second crankpins 107p, 107q, 107r having a central axis 107k at positions offset by an equal distance from the central axis 107b of the respective second crankpins 107c-107h.

Therefore, each central axis 106k, 107k of each of the first and second crankpins 106c-106h, 107c-107h of these first and second crankshaft members 106, 107, and each of the first and second crankpins 106p, 106q The central axes 106b, 107b of , 106r, 107p, 107q, 107r are arranged parallel to the input central axis O1 in the state of being attached to the continuously variable transmission mechanism BD.

In addition, each of the first and second crank pins 106c to 106h, 107c to 107h of each of the first and second crankshaft members 106, 107 is arranged such that their respective central axes 106k, 107k are aligned with the crank journals 106p, 106q, 106r, 107p. The center axes 106b, 107b of , 107q, 107r are respectively combined in such a way that they are centered at a predetermined angle (60° in this embodiment) in the circumferential direction.

In addition, in FIG. 3 , illustration of the first and second crank journals 106q and 107q is omitted.

In addition, as shown in FIG. 5, the two through-holes 104a, 104b of the respective eccentric disks 104 through which the first and second crankpins 106c-106h, 107c-107h penetrate are formed so that the two through-holes 104a, 104b are opposite to each other. They are adjacently arranged, and the middle point M of the through-holes 104a, 104b is offset from the first fulcrum O3. In addition, the two through-holes 104a, 104b of each eccentric disk 104 are respectively formed such that the middle point M of the through-holes 104a, 104b of the plurality of eccentric disks 104 is centered on the first fulcrum O3 at a predetermined angle in the circumferential direction (in this paper, 60° in one embodiment).

Specifically, among the six eccentric disks 104 in this embodiment, the eccentric disk 104A through which the first and second crankpins 106c and 107c penetrate and the eccentric disk 104D through which the first and second crankpins 106f and 107f penetrate are composed of The configuration is such that the line connecting the centers 104e, 104f of the through-holes 104a, 104b is located on the line passing through the first fulcrum O3. In addition, the eccentric disc 104B through which the first and second crank pins 106d and 107d penetrate, the eccentric disc 104C through which the first and second crank pins 106e and 107e penetrate, and the eccentric disc 104C through which the first and second crank pins 106g and 107g penetrate. The disk 104E and the eccentric disk 104F through which the first and second crank pins 106h and 107h pass are constituted by the following structure: the line connecting the middle point M and the first fulcrum O3 is connected to the two through holes 104a, 104a, The lines at the center 104e, 104f of 104b intersect.

Therefore, if each of the eccentric disks 104A to 104F at the eccentricity r is shown around the input central axis O1, each of the eccentric disks 104A to 104F has a positional relationship as shown in FIG. 6 . That is, in a state where the eccentricity r of the first fulcrum O3 serving as the center of each eccentric disc 104A to 104F with respect to the input central axis O1 is the same, each of the first and second crank pins 106c to 106h and 107c to 107h is positioned at the following positions: The positions where the central axes 106b, 107b are sequentially rotated 60° clockwise, and the eccentric disks 104A to 104F are also in a positional relationship where the input central axis O1 is sequentially rotated 60° clockwise.

In addition, the angle between the first and second crankpins 106c-106h, 107c-107h, or the angle between the through-holes 104a, 104b formed in the eccentric discs 104 and the first fulcrum O3 is connected with the central axis 106b, 107b as the center. The relationship between them (for example, the angle between the line connecting the middle point M of each through hole 104a, 104b and the first fulcrum O3, and the line connecting the centers 104e, 104f of the two through holes 104a, 104b) is determined by the eccentric disk 104 The number of eccentric discs 104 is determined by dividing 360 degrees by the number of eccentric disks 104.

The input shaft 151 is an integrally formed product consisting of: a cylindrical portion 151d splined to the end of the output shaft S; Crankshaft journals 106p, 107p of members 106, 107 are supported by two through-holes 151a, 151b rotatably.

In addition, the crankshaft journals 106q, 107q of the first and second crankshaft members 106, 107 located between the two eccentric discs 104C, 104D pass through the two first and second support holes 152a formed in the journal support member 152. , 152b are rotatably supported via sliding bearings 157 .

Further, driven gears 106a, 107a are formed on the crank journals 106r, 107r of the first and second crankshaft members 106, 107, and these driven gears 106a, 107a are coaxial with the input central axis O1 in the actuator 180. The pinion gears 180b of the rotation shaft 180a provided mesh with each other, and also mesh with the ring gear 115 provided around them.

In addition, the input shaft 151, the journal support member 152, and the ring gear 115, which support the two first and second crankshaft members 106 and 107 in a rotatable manner, are respectively connected to the transmission housing of the transmission not shown via the bearings 102, 105 and 103. Body 160 supports.

The driven gears 106a, 107a of the two first and second crankshaft members 106, 107 have the same number of teeth, and the pinion gear 180b is rotated by the actuator 180, whereby the two driven gears 106a, 107a rotate at the same rotational speed. The actuator 180 is composed of a DC motor, a reduction mechanism, and the like, and normally rotates the pinion gear 180b in synchronization with the rotation of the input shaft 151 . Therefore, as shown in (a) to (f) of FIG. , if the diameter of the eccentric disk 104 is set to D, the maximum amplitude W of the eccentric disk 104 is W=D+2·r. 7(a) to 7(f) show that the rotation angles of the first and second crankshaft members 106, 107 and the eccentric disk 104 are respectively set to α=0°, 60°, 120°, 180°, 240°, 300° states.

Also, the pinion gear 180b is relatively rotated with respect to the input shaft 151 by applying a rotational speed greater or smaller than the rotational speed of the input shaft 151 to the pinion gear 180b based on the synchronous rotational speed of the input shaft 151 and the pinion gear 180b. The rotation speed control by the actuator 180 is realized, for example, by controlling the reduction ratio obtained by multiplying the speed reduction ratio of the reduction mechanism (for example, a planetary gear) by the rotation speed of the actuator 180 with respect to the rotation speed of the input shaft 151 . The rotational speed of the gear 180b. At this time, when the pinion gear 180b and the input shaft 151 are synchronized without a rotation difference, the eccentricity r does not change.

Therefore, by supplying the pinion gear 180b with a rotational speed greater than or less than the rotational speed of the input shaft 151, the first and second crank journals 106r, 107r having the driven gears 106a, 107a rotate on their own, and the first crankpins 106c-106h and the first crankpins 106c-106h 2 The crank pins 107c to 107h rotate synchronously around the central axes 106b, 107b of the first and second crank journals 106r, 107r, respectively, to adjust the eccentricity r of the first fulcrum O3 relative to the input central axis O1.

In addition, the one-way clutch OWC has: a clutch inner 121 as an output member that rotates around an output center axis O2 deviated from the input center axis O1; an annular clutch outer 122 as an input member that receives the rotation direction from the outside. The power swings around the output center axis O2; as engaging members, a plurality of rollers 123 are inserted into the clutch outer member 122 and the clutch in order to set these clutch outer members 122 and clutch inner members 121 in a locked state or an unlocked state with each other. Between the inner parts 121; and the force applying part 126, which applies force to the direction of applying the locked state to the roller 123. When the rotation speed of the clutch member 121 is positive, the one-way clutch OWC transmits the rotational power input to the clutch outer member 122 to the clutch inner member 121, thereby converting the swing motion of the clutch outer member 122 into the clutch inner member 121. Rotational movement.

As shown in FIG. 1 , the clutch inner member 121 of the one-way clutch OWC is constituted as an integrally continuous member in the axial direction, however, the clutch outer member 122 is divided into a plurality in the axial direction, and is connected to the eccentric disc 104 and the connecting member 130 Correspondingly, the numbers are arranged to be able to swing independently in the axial direction. And, a roller 123 is inserted between the clutch outer 122 and the clutch inner 121 corresponding to each clutch outer 122 .

A protruding portion 124 is provided at one position in the circumferential direction on each of the ring-shaped clutch outer members 122 , and a second fulcrum O4 offset from the output center axis O2 is provided on the protruding portion 124 . In addition, a pin 125 is disposed on the second fulcrum O4 of each clutch outer 122 , and the terminal (other end) 132 of the connecting member 130 is rotatably connected to the clutch outer 122 by the pin 125 .

On one end side of the connecting member 130 , there is a ring portion 131 , and the inner periphery of the circular opening 133 of the ring portion 131 is rotatably fitted to the outer periphery of the eccentric disk 104 via the bearing 140 . Therefore, one end of the connecting member 130 is rotatably connected to the outer periphery of the eccentric disc 104, and the other end of the connecting member 130 is rotatably connected to the clutch outer member 122 provided on the one-way clutch OWC. The second fulcrum O4 constitutes a four-joint linkage mechanism with four nodes as the rotation points of the input central axis O1, the first fulcrum O3, the output central axis O2, and the second fulcrum O4. From the input shaft 151 via two The rotational motion given to the eccentric disc 104 by the first and second crankshaft members 106 and 107 is transmitted to the clutch outer member 122 as a swing motion of the clutch outer member 122 of the one-way clutch OWC, and the swing motion of the clutch outer member 122 is converted into a rotational motion of the clutch inner member 121 .

At this time, by using the actuator 180, the pinion gear 180b of the transmission ratio variable mechanism 112 composed of the two first and second crankshaft members 106, 107, the actuator 180, etc. is operated, whereby the eccentric disc 104 can be changed. The eccentricity r. Furthermore, by changing the eccentricity r, the swing angle θ2 of the clutch outer 122 of the one-way clutch OWC can be changed, thereby changing the ratio of the rotation speed of the clutch inner 121 to the rotation speed of the input shaft 151 (gear ratio i). Therefore, it is possible to change the gear ratio when the rotational power input to the input shaft 151 is transmitted as rotational power to the clutch inner 121 of the one-way clutch OWC via the eccentric disc 104 and the connecting member 130, and since the eccentricity r can be set to Set to zero, so the gear ratio can be set to infinity.

The shifting principle of the continuously variable transmission mechanism BD described above will be described with reference to FIG. 8 and FIG. 9 .

In (a) to (e) of FIG. 8 , the diagrams on the left show the rotation angles θc of the first and second crankshaft members 106 and 107 when the pinion gear 180b is relatively rotated in the eccentric disk 104A. The figure on the right side shows the central axes 106b, 107b (black circles) of the crankshaft journals 106r, 107r and the central axes 106k, 107k (white circles) of the first and second crankpins 106c, 107c. ) is a graph extracted from the graph on the left. In addition, in order to understand the shape easily, the first and second crankpins 106c and 107c are hatched, and in (b) to (e) of FIG. 8 , those shown in (a) of FIG. The pinion gear 180b shows the driven gears 106a, 107a in solid circles.

As shown in (a) of FIG. 8, in the eccentric disc 104A, when the rotation angle θc of the first and second crankshaft members 106, 107=0°, the central axes 106b, 107b of the crankshaft journals 106r, 107r are opposite to each other. The central axes 106k, 107k of the first and second crankpins 106c, 107c are shifted upward, and the input central axis O1 coaxial with the pinion 180b coincides with the first fulcrum O3 that is the center of the eccentric disk 104A. Therefore, the eccentricity r of the center (first fulcrum O3 ) of the eccentric disk 104 with respect to the input center axis O1 is zero, and the gear ratio i can be set to "infinity (∞)".

Next, as shown in Fig. 8(b) to Fig. 8(d), when the rotation angle θc of the first and second crankshaft members 106, 107 = 45°, 90°, 135°, the first and second 2 The central axes 106k, 107k of the crank pins 106c, 107c rotate in the same direction relative to the central axes 106b, 107b of the crank journals 106r, 107r, and the center of the eccentric disc 104 (first fulcrum O3) gradually moves away from the input central axis O1, The eccentricity r becomes larger gradually.

Then, as shown in (e) of FIG. 8, when the rotation angles of the first and second crankshaft members 106, 107 are θc=180°, the central axes 106b, 107b of the crankshaft journals 106r, 107r are respectively relative to the first and the central axes 106k, 107k of the second crank pins 106c, 107c are in the downward shifted position, the center of the eccentric disk 104 (the first fulcrum O3) is the farthest from the input central axis O1, and the eccentricity r becomes the largest, which can realize Small gear ratio.

(a) to (c) of FIG. 9 are views of the six eccentric disks 104A to 104F viewed from the actuator 180 side, and (a) of FIG. 9 shows the first fulcrum O3 and the In the state where the input center axis line O1 coincides and the eccentricity r is set to "zero", that is, when the transmission ratio i is set to be infinite, (b) of FIG. The fulcrum O3 is separated from the input central axis O1, and the eccentricity r is set to "middle", that is, the case where the gear ratio i is set to an intermediate gear ratio, Fig. 9(c) shows the state of the eccentric disc Each of the first fulcrums O3 of 104A to 104F is farthest from the input central axis O1, and the eccentric amount r is set to be "large", that is, the case where the gear ratio i is set to a small gear ratio.

Such adjustment of the eccentricity r based on the rotation angle θc of the first and second crankshaft members 106, 107 is achieved by controlling the rotational speed of the rotating shaft 180a of the actuator 180 shown in FIG. 1 by a control unit not shown. to carry out.

As shown in FIG. 10 , in the continuously variable transmission mechanism BD, a four-joint linkage mechanism is formed with four nodes of the input central axis O1, the first fulcrum O3, the output central axis O2, and the second fulcrum O4 as rotation points. The rotational motion applied to the eccentric disc 104 from the input shaft 151 is transmitted as an oscillating motion to the clutch outer 122 of the one-way clutch OWC, and the oscillating motion of the clutch outer 122 is converted into a rotational motion of the clutch inner 121 .

As shown in (a) of FIG. 11 , when the eccentric amount r of the eccentric disk 104 is set to be "large" and the first fulcrum O3 is rotated in the direction of the arrow around the input central axis O1, the unit can be increased. The swing angle θ2 of the clutch outer 122 to the clutch OWC can realize a small gear ratio i.

As shown in (b) of FIG. 11, when the eccentricity r of the eccentric disc 104 is set to be "medium", the swing angle θ2 of the clutch outer member 122 of the one-way clutch OWC can be made smaller than that of (a) of FIG. ) in the case of the swing angle θ2 is small, so that a larger gear ratio i can be realized than in the case of (a) in FIG. 11 .

As shown in (c) of Figure 11, when the eccentricity r of the eccentric disc 104 is set to be "small", the swing angle θ2 of the clutch outer member 122 of the one-way clutch OWC can be made smaller than that of (b) of Figure 11 ) in the case of the swing angle θ2 is small, so that a larger gear ratio i can be realized than in the case of (b) in FIG. 11 .

Therefore, the smaller the eccentricity r of the eccentric disk 104 is, the smaller the swing angle θ2 of the clutch outer member 122 is, and the larger the gear ratio i is, and when the eccentricity r of the eccentric disk 104 is "zero", the Since the swing angle θ2 of the clutch outer 122 of the one-way clutch OWC is "zero", the gear ratio i can be set to "infinity (∞)".

As shown in FIG. 10 , the clutch outer 122 of the one-way clutch OWC receives power applied from the eccentric plate 104 via the connecting member 130 to perform a swinging motion. When the input shaft 151 that rotates the eccentric disk 104 rotates once, the clutch outer 122 of the one-way clutch OWC swings back and forth once. As shown in FIG. 12 , the swing period of the clutch outer 122 of the one-way clutch OWC is always constant regardless of the value of the eccentricity r of the eccentric plate 104 . The swing angular velocity ω2 of the clutch outer 122 is determined by the rotational angular velocity ω1 of the eccentric disc 104 (input shaft 151 ) and the eccentricity r.

The ring portions 131 of the plurality of connecting members 130 connecting the input shaft 151 and the one-way clutch OWC are rotatably connected to a plurality of eccentric disks 104 arranged at equal intervals in the circumferential direction around the input center axis O1. Therefore, each eccentric disk 104 The swinging motion of the clutch outer member 122 of the one-way clutch OWC is sequentially performed with a fixed phase as shown in FIG. 13 due to the rotational motion.

At this time, the transmission of power (torque) from the clutch outer member 122 to the clutch inner member 121 of the one-way clutch OWC exceeds the clutch inner member 121 only in the forward direction (arrow RD1 direction of FIG. 10 ) of the clutch outer member 122. It is only carried out under the condition of positive speed. That is, in the one-way clutch OWC, when the rotation speed of the clutch outer member 122 becomes higher than the rotation speed of the clutch inner member 121, the meshing (locking) of the clutch outer member 122 and the clutch inner member 121 via the roller 123 starts to occur, and the clutch The power of the outer member 122 is transmitted to the clutch inner member 121 to generate driving force.

After the driving by one connecting member 130 ends, the rotation speed of the clutch outer member 122 is lower than that of the clutch inner member 121, and the lock by the roller 123 is released by the driving force of the other connecting member 130 and returns to free. state (idling state). By sequentially performing the above operations according to the number of connecting members 130, the swing motion is converted into a rotational motion in one direction. Therefore, the power of the clutch outer 122 is sequentially transmitted to the clutch inner 121 only at the timing exceeding the rotation speed of the clutch inner 121 , and an approximately average rotational power is applied to the clutch inner 121 substantially smoothly.

In addition, as shown in (a) to (c) of FIG. 11 , in the continuously variable transmission mechanism BD of the four-joint link mechanism type, the gear ratio (gear ratio) can be determined by changing the eccentricity r of the eccentric disk 104 . In this case, by setting the eccentricity r to zero, the gear ratio i can be set to infinity (∞), and even during the rotation of the output shaft S of the drive source, the The swing angle θ2 of 122 is set to zero. That is, even if the output shaft S (see FIG. 1 ) of the drive source rotates, the rotation speed of the clutch inner 121 of the one-way clutch OWC can be set to zero.

Next, an embodiment of the present invention will be described with reference to FIGS. 14 to 19 . In addition, the basic structure of the continuously variable transmission mechanism BD' of the present embodiment is the same as that of the continuously variable transmission mechanism BD of the reference example except that the structures of the first and second crankshaft members and eccentric discs and the number of journal support members 152 are different. . Therefore, below, referring also to FIGS. 4 to 13 which are configurations of the reference example, the parts different from the continuously variable transmission mechanism BD of the reference example will be mainly described. Therefore, for the same or equivalent parts as those of the continuously variable transmission mechanism BD of the reference example, the same reference numerals or corresponding reference numerals are attached, and descriptions are simplified or omitted.

As shown in FIGS. 14 to 17 , the first crank member 16 of this embodiment has a plurality of (six in this embodiment) first crank pins 16c to 16h arranged at intervals of 60° in the circumferential direction. Each of the first crankpins 16c to 16h is connected via a plurality of (seven in this embodiment) first crankpins 16p to 16v arranged alternately across the first crankpins 16c to 16h. The plurality of first crank journals 16p to 16v has a center axis 16b at a position deviated from the center axis 16k of each of the first crank pins 16c to 16h by an equal distance. In other words, the plurality of first crank pins 16c to 16h are arranged at equal intervals in the circumferential direction around the center axis 16b of the plurality of first crank journals 16p to 16v. The outer diameters D1 of the first crankpins 16c to 16h are all equal, or gradually increase from one side to the other side in the axial direction.

A driven gear 16a is formed on the first crank journal 16p on the side of the actuator 180, and the driven gear 16a meshes with a pinion 180b of the rotating shaft 180a provided coaxially with the input center axis O1, and is also provided with the A ring gear 115 meshes around these components. The first crank journal 16 v located on the output shaft S side is rotatably supported in a through hole 151 a formed in the input shaft 151 .

Each of the first crank pins 16 c to 16 h rotatably penetrates through one of the two first and second through holes 14 a , 14 b formed in the corresponding eccentric disk 14 via a sliding bearing 155 , respectively. In addition, in FIGS. 14 to 19 , the sliding bearing 155 is omitted.

Therefore, the first crankshaft member 16 of the present embodiment corresponds to the first crankshaft member 106 of the continuously variable transmission mechanism of the reference example, the driven gear 16a corresponds to the driven gear 106a, the central axis 16b corresponds to the central axis 106b, and the first crankpin 16c ˜16h correspond to first crank pins 106c to 106h, central axis 16k corresponds to central axis 106k, and first crank journals 16p, 16s, 16v correspond to first crank journals 106r, 106q, 106p. The first crank journals 16q, 16r, 16t, and 16u of the present embodiment have structures that do not exist in the first crank member 106 of the continuously variable transmission mechanism of the reference example.

With regard to the plurality of first crank journals 16p to 16v, projected portions N1 obtained by projecting the first crank journals 16p to 16v in the axial direction are respectively located on the first crank pins 16c to 16 connected to the first crank journals 16p to 16v. 16h within the outline (contour) N2. More specifically, for example, as shown in (b) of FIG. 18 , the projection portion N1 obtained by projecting the first crank journal 16q in the axial direction is located at the first crank pin 16c connected to the first crank journal 16q. , 16d (not shown) within the outline (outline outline) N2. This relationship is also the same for the first crank journals 16p, 16r to 16v. Moreover, in this embodiment, the case where all the outer diameters D1 of the 1st crankpins 16c-16h are equal is shown.

Like the first crank member 16, the second crank member 17 has a plurality of (six in this embodiment) first crank pins 17c to 17h arranged at intervals of 60° in the circumferential direction. The respective second crank pins 17c to 17h are connected together via a plurality of (seven in this embodiment) second crank journals 17p to 17v arranged alternately across the second crank pins 17c to 17h. The plurality of second crank journals 17p to 17v has a center axis 17b at a position deviated from the center axis 17k of each of the second crank pins 17c to 17h by an equal distance. In other words, the plurality of second crank pins 17c to 17h are arranged at equal intervals in the circumferential direction around the center axis 17b of the second crank journals 17p to 17v. The outer diameters D3 of the second crankpins 17c to 17h are all equal, or gradually increase from one side to the other side in the axial direction.

A driven gear 17a is formed on the second crank journal 17p on the side of the actuator 180, and the driven gear 16a meshes with a pinion 180b of a rotating shaft 180a coaxial with the input center axis O1 and is also provided with A ring gear 115 meshes around these components. The second crank journal 17 v located on the output shaft S side is rotatably supported in a through hole 151 b formed in the input shaft 151 .

Each of the second crank pins 17c to 17h rotatably penetrates through the other second through hole 14b of the two first and second through holes 14a and 14b formed in the corresponding eccentric disk 14 via a sliding bearing 155 . In addition, in FIGS. 14 to 19 , the sliding bearing 155 is omitted.

Therefore, the second crank member 17 of the present embodiment corresponds to the second crank member 107 of the continuously variable transmission mechanism of the reference example, the driven gear 17a corresponds to the driven gear 107a, the central axis 17b corresponds to the central axis 107b, and the second crank pin 17c ˜17h correspond to the second crank pins 107c to 107h, the central axis 17k corresponds to the central axis 107k, and the second crank journals 17p, 17s, and 17v correspond to the second crank journals 107r, 107q, and 107p. The second crank journals 17q, 17r, 17t, and 17u of the present embodiment have structures that do not exist in the second crank member 107 of the continuously variable transmission mechanism of the reference example.

With regard to the plurality of second crank journals 17p to 17v, the projected portions N1 obtained by projecting the second crank journals 17p to 17v in the axial direction are located on the second crank pins 17c to 17c connected to the second crank journals 17p to 17v, respectively. 17h within the contour (contour) N2. More specifically, for example, as shown in (b) of FIG. 18 , the projected portion N1 obtained by projecting the second crank journal 17q in the axial direction is located at the second crank pin 17c connected to the second crank journal 17q. , 17d (not shown.) within the outline (outline outline) N2. This relationship is also the same for the second crank journals 17p, 17r to 17v. In addition, in this embodiment, the case where all the outer diameters D3 of the second crankpins 17c to 17h are equal is shown.

The eccentric directions and eccentric amounts of the first and second crank pins 16c to 16h, 17c to 17h in this embodiment are the same as those of the first and second crank pins 106c to 106h, 107c～107h are the same.

As shown in FIG. 17 , the axial length L2 of the first and second crank journals 16p to 16v, 17p to 17v is set to be equal to or larger than the axial width L1 of the eccentric disc 14 described later. L1 is long. Accordingly, the eccentric disk 14 can move in the radial direction (direction perpendicular to the central axes 16b, 17b) between the first and second crankpins (for example, 16c and 16d, 17c and 17d) that face each other and are adjacent to each other.

As shown in FIGS. 14 and 15 , in the axial direction, the first and second crankshaft journals 16q to 16u and 17q to 17u of the first and second crankshaft members 16 and 17 with the same phase are rotatable via sliding bearings 157, respectively. The first and second support holes 152a, 152b formed in the journal support member 152 are fitted in such a manner. In addition, in FIGS. 14 to 19 , the slide bearing 157 is omitted.

The plurality of journal support members 152 are respectively supported by a transmission case 160 of the transmission via bearings 105 .

In addition, each eccentric disk 14 is fitted to the ring portion 131 of the connection member 130 via a bearing 140 .

As shown in (a) of FIG. 18 , like the eccentric disk 104 of the reference example, the first and second through-holes 14 a and 14 b of the eccentric disk 14 are formed in parallel. However, the eccentric disk 14 of this embodiment has the characteristic that it is not divided but integrally formed. The first crank pins 106c to 106h are respectively rotatably fitted in the first through holes 14a of the plurality of eccentric disks 14 . In addition, the second crank pins 107c to 107h are respectively rotatably fitted in the second through-holes 14b of the plurality of eccentric disks 14 .

As shown in FIG. 18 , regarding the first and second crankshaft members 16 and 17 of the present embodiment, as described above, the first crank journals 16p to 16v are arranged on the first crankpins 16c to 16v when viewed from the axial direction. Within the contour N2 of 16h, the respective second crank journals 17p to 17v are arranged within the contour N2 of the second crankpins 17c to 17h. In addition, the outer diameter D1 of the first crank pins 16c to 16h of the first crank member 16 is approximately the same as the diameter D5 of the first through hole 14a of the corresponding eccentric disc 14, and the second crank pins 17c to 16h of the second crank member 17 The outer diameter D3 of 17h is substantially the same as the hole diameter D6 of the second through-hole 14b of the corresponding eccentric disc 14 .

Accordingly, the eccentric disk 14 can be assembled by inserting the first and second crankshaft members 16 , 17 into the first and second through-holes 14 a , 14 b of the eccentric disk 14 from one end side, respectively.

Specifically, as shown in FIG. 16 and FIG. 17, first, the first and second crank pins 16h, 17h of the first and second crankshaft members 16, 17 are inserted to the first and second pins on the innermost side in the direction of insertion. In the first and second through-holes 14a, 14b of the eccentric disk 14 corresponding to (fitting) the second crank pins 16c, 17c, the eccentric disk 14 is moved in the axial direction until the eccentric disk 14 is about to be connected to the first of the second crankpin. and the side surfaces of the second crankpins 16g and 17g (the right sides in the figure) abut against each other. At this time, the eccentric disk 14 is at a position corresponding to the first and second crank journals 16u and 17u in the axial direction.

Next, the eccentric disk 14 is moved in the radial direction so that the axial centers of the first and second through holes 14a, 14b and the first and second crank pins 16g, 17g coincide. At this time, since the axial length L2 of the first and second crank journals 16u, 17u is longer than the axial width L1 of the eccentric disk 14, the radial movement of the eccentric disk 14 is not hindered. Then, the first and second crank pins 16g, 17g are inserted into the first and second through holes 14a, 14b, and penetrate to the eccentric disk 14, which is about to be connected with the third crank pins 16f, 17f. side contact.

Hereinafter, similarly, the eccentric disk 14 is moved alternately in the axial direction and the radial direction while passing through the first and second crank pins 16f, 17f, 16e, 17e, 16d, 17d, so that the first and second crankpins of the eccentric disk 14 are The second through-holes 14a, 14b are fitted with the first and second crank pins 16c, 17c on the innermost side in the insertion direction.

Next, while moving the eccentric discs 14 corresponding to the first and second crankpins 16d, 17d, which are numbered second from the back side, alternately in the radial direction and the axial direction as described above, the first and second 2 The crankshaft members 16, 17 are inserted through the first and second through-holes 14a, 14b, and the first and second through-holes 14a, 14b of the eccentric disk 14 are fitted with the first and second crankpins 16d, 17d.

In the same manner below, the remaining first and second crank pins 16e to 16h, 17e to 17h are fitted into the first and second through-holes 14a and 14b of the corresponding eccentric disks 14, respectively. FIG. 19 shows a state in which the eccentric disks 14 are attached to the first and second crank pins 16c of the first and second crankshaft members 16 and 17 in a state where the eccentric amount r of each eccentric disk 14 is zero. ~16h, 17c~17h, and then assemble the journal support member 152 between the eccentric disks 14.

In this way, the eccentric disk 14, which is not divided but constituted by a single member, can be assembled to the first and second crankshaft members 16, 17, so that the support rigidity of the eccentric disk 14 can be improved, and the first and second crankshaft members can be supported with high precision. The second crankshaft components 16, 17. As a result, fluctuations in the eccentric amount r of the eccentric disk 104 , that is, the gear ratio are reduced, and stable gear shifting can be realized.

In addition, in the assembly of the eccentric disk 14, if the outer diameters D1 and D3 of the first and second crank pins 16c to 16h and 17c to 17h are formed from one side to the other side in the axial direction (from the end side in the insertion direction), The first and second crankpins 16c-16h, 17c-17h that are closer to the front side than the first and second crankpins 16c-16h, 17c-17h corresponding to the eccentric disk 14 to be assembled The outer diameters D1 and D3 of 16h, 17c to 17h are smaller than the diameters D5 and D6 of the first and second through holes 14a and 14b of the eccentric disk 14, so that the insertion of the eccentric disk 14 becomes easier and the assembly efficiency is improved. .

As described above, according to the continuously variable transmission mechanism BD of this embodiment, the outer diameters D1 of the plurality of first crank pins 16c to 16h are all equal or become larger from one side to the other in the axial direction, and the plurality of first crankpins The crank journals 16p to 16v are arranged so that the projected portion N1 obtained by projecting the first crank journals 16p to 16v in the axial direction is positioned on the first crank pins 16c to 16h connected to the first crank journals 16p to 16v. In addition, the outer diameters D3 of the plurality of second crankpins 17c to 17h are all equal or become larger from one side to the other in the axial direction, and the plurality of second crankpins 17p to 17v are provided respectively. A projection portion N1 obtained by projecting the second crank journals 17p to 17v in the axial direction is located within the outline N2 of the second crank pins 17c to 17h connected to the second crank journals 17p to 17v. In addition, since the axial width L1 of the plurality of eccentric disks 14 is smaller than the axial length L2 of the first crank journals 16p to 16v and the second crank journals 17p to 17v, respectively, the eccentric discs 14 can be divided without radial division. The integrally formed eccentric disk 14 is sequentially inserted and assembled from one side toward the other side of the first and second crankshaft members 16 and 17 . Therefore, it is possible to prevent the decrease in the dimensional accuracy of the inner diameters of the first and second through holes 14a, 14b through which the first and second crank pins 16c-16h, 17c-17h pass through due to the opening of the eccentric disc 14, and to prevent eccentricity. The change of the amount r can be suppressed, thereby suppressing the influence on the gear ratio. In addition, since the eccentric disk 14 is integrally formed, the number of parts can be reduced.

In addition, since the first and second through-holes 14a, 14b formed in the eccentric disk 14 do not communicate with each other, the rigidity of the eccentric disk 14 can be increased, and the variation of the eccentricity r of the eccentric disk 14 can be more reliably prevented.

In addition, the present invention is not limited to the above-described embodiments, and appropriate modifications, improvements, and the like can be made. In addition, as long as the present invention can be realized, the material, shape, size, number, arrangement location, etc. of each component in each of the above-mentioned embodiments may be arbitrary and are not limited.

For example, in the eccentric disc 14 of the above-mentioned embodiment, the first and second through-holes 14a, 14b through which the first and second crank pins 16c-16h, 17c-17h pass through are not communicated. The structure is such that the first and second through-holes 14a and 14b communicate with each other and provide a single long hole through which both of the first and second crank pins 16c to 16h and 17c to 17h pass.

Claims (2)

1. a stepless speed changing mechanism, it has:

Power shaft, this power shaft accepts to rotate around input central axis from the rotary power of power source generation；

Multiple eccentric discs, the plurality of eccentric disc has the 1st fulcrum at respective center, and each 1st fulcrum is in this input Circumferentially about being disposed at equal intervals of central axis, and inclined relative to described input central axis of each 1st fulcrum Heart amount can be changed, and the plurality of eccentric disc is defeated with described around this input central axis while keeping this offset Enter axle to rotate together, and, the plurality of eccentric disc is respectively formed with described input centerline axis parallel prolong The 1st through hole stretched and the 2nd through hole；

1st crankshaft component, the 1st crankshaft component has multiple 1st crankpin and multiple 1st crankshaft journal, described The most through described 1st through hole formed on the plurality of eccentric disc of multiple 1st crankpins, and that This links, and the plurality of 1st crankshaft journal is offseting the position of equidistance from the central axis of this each 1st crankpin Place has central axis；

2nd crankshaft component, the 2nd crankshaft component has multiple 2nd crankpin and multiple 2nd crankshaft journal, described The most through described 2nd through hole formed on the plurality of eccentric disc of multiple 2nd crankpins, and that This links, and the plurality of 2nd crankshaft journal is offseting the position of equidistance from the central axis of this each 2nd crankpin Place has central axis；

One-way clutch, this one-way clutch has around the output center axis rotation deviateing described input central axis Output block, by accept the power of direction of rotation from outside and around described output center axis oscillating input block, And make these input blocks and output block become mutually lock-out state or the joint elements of non-locking state, when described During the rotating speed of the forward that the rotating speed of the forward of input block exceedes described output block, this one-way clutch will enter into institute The rotary power stating input block is transferred to described output block, thus the oscillating motion of described input block is converted to The rotary motion of described output block；

Multiple connecting members, the respective one end of the plurality of connecting member rotatably connects centered by described 1st fulcrum Knot is in the periphery of each described eccentric disc, and the respective other end of the plurality of connecting member is rotatably linked at described list The 2nd fulcrum that the position deviateing described output center axis on the input block of clutch is arranged, thus, will The rotary motion swing as the input block of described one-way clutch of described eccentric disc is put on from described power shaft Motion is transferred to this input block；And

Gear ratio changeable mechanism, this gear ratio changeable mechanism possesses actuator, and described actuator makes described 1st crankpin Synchronously rotate centered by described 1st crankshaft journal and the 2nd crankshaft journal respectively with described 2nd crankpin, adjust Save described 1st fulcrum offset relative to described input central axis, thus change and be transferred to institute from described eccentric disc Stating the pendulum angle of the oscillating motion of the input block of one-way clutch, thus, the change of described gear ratio changeable mechanism exists The rotary power being input to described power shaft is transmitted as rotary power via described eccentric disc and described connecting member To the gear ratio during output block of described one-way clutch, and, owing to described offset can be set as zero, It is thus possible to gear ratio is set as infinity, wherein,

The external diameter of the plurality of 1st crankpin is the most equal or becomes big from side towards opposite side in the axial direction,

The external diameter of the plurality of 2nd crankpin is the most equal or becomes big from side towards opposite side in the axial direction,

The plurality of 1st crankshaft journal is respectively arranged to: carry out described 1st crankshaft journal vertically projecting gained To projection section be positioned at the profile of described 1st crankpin being connected with the 1st crankshaft journal,

The plurality of 2nd crankshaft journal is respectively arranged to: carry out described 2nd crankshaft journal vertically projecting gained To projection section be positioned at the profile of described 2nd crankpin being connected with the 2nd crankshaft journal,

The axial width of the plurality of eccentric disc axial than described 1st crankshaft journal and described 2nd crankshaft journal respectively Length is little.

Stepless speed changing mechanism the most according to claim 1, wherein,

Described 1st through hole formed on described eccentric disc does not connects with described 2nd through hole.