CN105041815A - Continuously variable transmission device - Google Patents

Abstract

The invention provides a continuously variable transmission. In a continuously variable transmission having a crank mechanism of a four-bar mechanism type, an effective pressure receiving surface that receives pressure from a connecting pin is enlarged. In a continuously variable transmission (1) with an input shaft (2), an output shaft (3), a radius of rotation adjustment mechanism (4), a connecting rod (15) and a swing connecting rod (18), the connecting pin (19) will connect The end of the rod (15) is rotatably connected to the swing end (18a) of the swing link (18), and the anti-loosening mechanism for preventing the fall of the connecting pin (19) has: a groove (19a), which is arranged on the connecting pin (19a). The outer peripheral surface of the pin (19); and the anti-dropping pin (21), which is inserted into the output side annular portion (15b) at a position corresponding to the groove portion (19a) in the axial direction of the connecting pin (19). The hole portion (15c) is in contact with the inner surface of the groove portion (19a).

Description

CVT

technical field

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

Background technique

Conventionally, a continuously variable transmission has been proposed which has: an input shaft; an output shaft arranged parallel to the input shaft; The rotation radius adjustment mechanism includes a rotating part that can rotate freely around the rotation center axis of the input shaft, and can freely adjust the rotation radius of the rotating part. The swing link is pivotally supported on the output shaft and is provided with an annular swing The connecting rod includes an input-side end rotatably connected to the rotating part and an annular output-side end connected to the swing end, and the crank-link mechanism converts the rotational motion of the input shaft into swing The swing movement of the connecting rod; the one-way rotation prevention mechanism, which fixes the swing connecting rod relative to the output shaft when the swing connecting rod is about to rotate to one side relative to the output shaft with the center axis of rotation of the output shaft as the center, and the swing connecting rod To rotate to the other side, the swing connecting rod is idly rotated relative to the output shaft; and a cylindrical or cylindrical connecting pin that penetrates the swing end and the output side end of the connecting rod in the direction of the rotation center axis of the output shaft, In this continuously variable transmission, the swing end and the output side end are connected so as to be relatively rotatable, and the gear ratio is changed by changing the radius of rotation of the rotating part (for example, refer to Patent Document 1).

In the continuously variable transmission configured in this way, relative rotation is enabled by inserting the connecting pin into the hole in the annular swing end of the swing link and the hole in the annular output side end of the connecting rod.

As a structure for holding the connecting pin so as not to fall off, a structure in which the length of the connecting pin in the axial direction is shorter than the length of the hole at the swing end of the swing link or the output side end of the link is considered. A circumferential groove is provided on the inner peripheral surface of the hole, and a C-shaped annular member is placed in the groove as a stopper for preventing the connection pin from falling off, and the annular member is brought into contact with the end surface of the connection pin.

According to this configuration, the output side end of the connecting rod can be rotatably connected to the swinging end of the swinging link, and the connection between the connecting rod and the swinging link and its release can be easily performed. Manufacturing of continuously variable transmissions.

Existing patent documents

patent documents

Patent Document 1: Japanese Patent Laid-Open No. 2012-251613

Contents of the invention

But, under the situation that utilizes above-mentioned structure to prevent that connecting pin comes off, because must dispose ring-shaped member so as to abut against the end surface of connecting pin, therefore, must shorten the space that is used for arranging ring-shaped member and the space for forming of connecting pin. The amount of space for fitting the groove of the annular member.

Therefore, the contact area between the peripheral surface of the connecting pin and the inner peripheral surface of the hole at the swing end portion becomes smaller than that of a configuration in which no annular member is arranged. That is, when the swing link is swung, there arises a problem that the entire inner peripheral surface of the hole at the output side end of the connecting rod or the swing end of the swing link cannot be used as an effective pressure receiving surface.

The present invention has been made in view of the above circumstances, and an object of the present invention is to realize a structure capable of increasing the effective pressure-receiving surface receiving pressure from the connecting pin in the above-mentioned four-bar mechanism type continuously variable transmission.

The present invention is a continuously variable transmission having: an input shaft; an output shaft disposed parallel to the input shaft; a crank link mechanism having a rotation radius adjustment mechanism, a swing link, and a connecting rod The radius of rotation adjustment mechanism includes a rotating part that can freely rotate around the central axis of rotation of the input shaft, and can freely adjust the radius of rotation of the rotating part, and the swing link is pivotally supported by the output shaft and is provided with a ring-shaped swing end, the connecting rod includes an input-side end rotatably connected to the rotating part and a ring-shaped output-side end connected to the swing end, and the crank The link mechanism converts the rotary motion of the input shaft into the swing motion of the swing link; the one-way rotation prevention mechanism is relatively to the swing link with the rotation center axis of the output shaft as the center fixing the swing link relative to the output shaft when the output shaft is to be rotated to one side, and idling the swing link relative to the output shaft when the swing link is to be rotated to the other side; and A columnar or cylindrical connecting pin that passes through the swing end of the swing link and the output side end of the connecting rod in the direction of the rotation center axis of the output shaft, and connects the The swing end and the output-side end are connected so as to be relatively rotatable. The continuously variable transmission changes the transmission ratio by changing the radius of rotation of the rotating part. The continuously variable transmission has a connecting pin detachment prevention mechanism. The pin detachment prevention mechanism restricts the movement of the connection pin relative to the output side end of the connecting rod in the axial direction of the connection pin, and the detachment prevention mechanism of the connection pin is composed of the following parts: a groove part, which provided on the outer peripheral surface of the connecting pin so as to extend in a direction perpendicular to the axial direction of the connecting pin; a hole at a position corresponding to the groove in the axial direction of the connecting pin provided at the output-side end of the connecting rod so as to extend in a direction perpendicular to the axial direction of the connecting pin; In a state where the hole is in contact with the inner surface of the groove.

In the connecting pin detachment prevention mechanism of the present invention, a part of the detachment prevention pin inserted into the hole provided on the output side end of the connecting rod abuts against the inner surface of the groove provided on the outer peripheral surface of the connecting pin, Prevent movement (dropping) of the connecting pin in its axial direction.

Therefore, the present invention does not need to shorten the space for arranging the ring-shaped member and form a space for inserting the connecting pin as in the case of using the ring-shaped member that must be arranged to be in contact with the end surface of the connecting pin as the connecting pin detachment prevention mechanism. The amount of space in the groove of the ring member.

Therefore, according to the present invention, when the swing link is swung, substantially the entire inner peripheral surface of the hole at the output side end of the connecting rod or the swing end of the swing link can be used as an effective pressure receiving surface.

And, because it is not a structure in which the parts for preventing falling out are arranged in contact with the end surface of the connecting pin, but a structure in which the connecting pin is locked with one preventing pin for falling out, therefore, one part for preventing falling out, that is, is used. Can. Thereby, the simplification of the connection pin detachment preventing mechanism can be realized.

In addition, in the continuously variable transmission according to the present invention, it is preferable that the swing link has an annular portion, the output shaft is disposed on the inner peripheral side of the annular portion, and the outer peripheral surface of the annular portion is provided with Even when the swinging end portion moves along the hole until one end of the locking pin abuts against the outer peripheral surface of the annular portion, the locking pin is in contact with the groove. butt against the inner surface of the part.

Therefore, even when the swing angle of the swing link becomes the maximum and the drop-off preventing pin moves along the hole, the drop-off preventing pin abuts against the outer peripheral surface of the annular portion of the swing link so as not to fall off. Also in this case, the state where the anti-dropping pin abuts on the inner surface of the groove part can be maintained. As a result, movement of the connecting pin relative to the connecting rod in the axial direction is reliably restricted.

Furthermore, in the continuously variable transmission of the present invention, it is preferable that when the swing link is about to rotate around the rotation center axis of the output shaft so that the swing end is separated from the input shaft, the The one-way rotation prevention mechanism fixes the swing link relative to the output shaft, and when the swing link is about to rotate in such a way that the swing end approaches the input shaft, the one-way rotation prevention mechanism The swing link is caused to idle with respect to the output shaft, and the hole is provided at a position farther from the input shaft than the center of the connecting pin.

Alternatively, preferably, when the swing link is about to rotate around the rotation center axis of the output shaft so that the swing end is close to the input shaft, the one-way rotation preventing mechanism The swing link is fixed relative to the output shaft, and when the swing link is about to rotate such that the swing end is away from the input shaft, the one-way rotation preventing mechanism makes the swing link relative to the output shaft. The output shaft idles, and the hole is provided at a position closer to the input shaft than the center of the connecting pin.

Accordingly, since the position where the hole is formed is located at a position where relatively low pressure is generated, it is possible to suppress a reduction in the durability of the connecting rod even if the hole is formed.

Description of drawings

FIG. 1 is a cross-sectional view showing an embodiment of a continuously variable transmission of the present invention.

FIG. 2 is an explanatory view showing the rotation radius adjustment mechanism, the connecting rod, and the swing link according to the present embodiment from the axial direction.

3A to 3D are explanatory diagrams illustrating changes in the eccentricity of the rotation radius adjustment mechanism of this embodiment, FIG. 3A shows the case where the rotation radius is "maximum", and Fig. 3B shows the case where the rotation radius is "medium". FIG. 3C shows a case where the radius of rotation is "small", and Fig. 3D shows a case where the radius of rotation is "0".

4A to FIG. 4C are explanatory diagrams showing the relationship between the variation of the eccentric amount of the rotation radius adjusting mechanism and the swing angle θ2 of the swing motion of the swing link according to the present embodiment, and FIG. 4A shows the swing link when the eccentric amount is the largest. Fig. 4B shows the swing angle of the swing movement of the swing link when the eccentricity is medium, and Fig. 4C shows the swing angle of the swing movement of the swing link when the eccentricity is small.

Fig. 5 is a cross-sectional view along line VV in Fig. 2 .

FIG. 6 is a cross-sectional view along line VI-VI in FIG. 5 .

FIG. 7 is a cross-sectional view illustrating a state changed from the state of FIG. 6 .

8A to FIG. 8B are cross-sectional views showing the connection pin detachment prevention mechanism when the swing angle of the swing link in this embodiment is at the maximum from the axis direction, and FIG. 8A shows the connection when the swing link swings to the outer dead center from the axis direction. Pin anti-off mechanism, Fig. 8B shows the connecting pin anti-off mechanism when the swing link swings to the inner dead point from the axial direction.

Label description

1: CVT; 2: Input shaft; 2a: Notch hole; 3: Output shaft; 4: Rotation radius adjustment mechanism; 5: Cam disc; 6: Rotating disc (rotating part); tooth; 7: pinion shaft; 7a: external tooth; 8: differential mechanism (planetary gear mechanism); 9: sun gear; 10: first ring gear; 11: second ring gear; 12: stepped pinion; 12a: Large diameter portion; 12b: Small diameter portion; 13: Planetary carrier; 14: Drive source (motor); 14a: Rotary shaft; 15: Connecting rod; 15a: Input side annular portion (input side end); 15b: Output side annular part (output side end); 15c: Hole part (coupling pin detachment prevention mechanism); 16: Roller bearing; 17: One-way clutch (one-way rotation preventing mechanism); 18: Swing link; 18a : swing end; 18b: protruding piece; 18c: through hole; 18d: groove; 18e: annular portion; 18f: outer peripheral surface; 19: connecting pin; Link mechanism; 21: anti-off pin (link pin anti-off mechanism); P1: rotation center axis; P2: center point of cam disc; P3: center point of rotating disc; Ra: distance between P1 and P2; Rb: distance between P2 and P3 distance; R1: eccentricity (distance between P1 and P3); θ2: swing range.

Detailed ways

Next, a continuously variable transmission according to an embodiment of the present invention will be described.

Referring to FIGS. 1 and 2 , a continuously variable transmission 1 according to the present embodiment has a hollow input shaft 2 which rotates about its central axis by receiving rotational power from a vehicle drive source such as an internal combustion engine or an electric motor (not shown). P1 rotates at the center; the output shaft 3 is arranged parallel to the input shaft 2, and transmits rotational power to the driving wheels (not shown) of the vehicle through the differential gear and transmission shaft outside the figure; and 6 rotation radius adjustment mechanisms 4, They are set on the input shaft 2.

Each rotation radius adjusting mechanism 4 is constituted by a cam plate 5 and a rotary plate 6 (rotary portion). The cam plates 5 are disk-shaped, and are provided in sets of two on the input shaft 2 so as to be eccentric with respect to the rotation center axis P1 and to rotate integrally with the input shaft 2 . Each set of cam disks 5 is set to have a phase difference of 60 degrees, and is arranged so that six sets of cam disks 5 make one turn around the input shaft 2 in the circumferential direction. In addition, a disk-shaped rotating disk 6 is eccentrically and rotatably fitted over each set of cam disks 5 , and the rotating disk 6 has a housing hole 6 a for accommodating the cam disk 5 .

Set the center point of the cam plate 5 as P2, set the center point of the rotary plate 6 as P3, the rotary plate 6 is eccentric relative to the cam plate 5, and make the distance Ra between the rotation center axis P1 and the center point P2 the same as the center point The distance Rb between P2 and the center point P3 is the same.

Internal teeth 6 b are provided in the receiving holes 6 a of the rotating disk 6 , and the internal teeth 6 b are located between the cam disks 5 of one set. The input shaft 2 is formed with a cutout hole 2 a which is located between the cam plates 5 of one set and communicates with an inner peripheral surface and an outer peripheral surface at a portion facing the eccentric direction of the cam disks 5 .

Inside the hollow input shaft 2 , a pinion shaft 7 is arranged rotatably relative to the input shaft 2 . The pinion shaft 7 is arranged concentrically with the input shaft 2 and has external teeth 7 a at a position corresponding to the rotating disk 6 . The external teeth 7 a of the pinion shaft 7 mesh with the internal teeth 6 b of the rotary disk 6 via the cutout hole 2 a of the input shaft 2 .

The differential mechanism 8 is connected to the pinion shaft 7 . The differential mechanism 8 is composed of a planetary gear mechanism, and has: a sun gear 9; a first ring gear 10 connected to the input shaft 2; a second ring gear 11 connected to the pinion shaft 7; The stepped pinion 12 is supported so as to be rotatable and revolvable. The stepped pinion 12 has a large-diameter portion 12 a meshing with the sun gear 9 and the first ring gear 10 and a small-diameter portion meshing with the second ring gear 11 12b constitutes.

A rotating shaft 14 a of a drive source 14 constituted by a motor for the pinion shaft 7 is connected to the sun gear 9 . When the rotation speed of the drive source 14 is the same as that of the input shaft 2, the sun gear 9 and the first ring gear 10 rotate at the same speed, and the sun gear 9, the first ring gear 10, the second ring gear 11 and the planetary carrier 13 These four elements are in a locked state in which they cannot rotate relative to each other, and the pinion shaft 7 connected to the second ring gear 11 rotates at the same speed as the input shaft 2 .

When the rotation speed of the drive source 14 is slower than the rotation speed of the input shaft 2, the rotation speed of the sun gear 9 is Ns, the rotation speed of the first ring gear 10 is Nr1, and the gear ratio between the sun gear 9 and the first ring gear 10 ( When the number of teeth of the first ring gear 10/the number of teeth of the sun gear 9 is j, the rotational speed of the carrier 13 becomes (j·Nr1+Ns)/(j+1). Furthermore, when the gear ratio between the sun gear 9 and the second ring gear 11 ((number of teeth of the second ring gear 11/number of teeth of the sun gear 9)×(number of teeth of the large-diameter portion 12a of the stepped pinion 12/small-diameter portion 12b When the number of teeth)) is k, the rotational speed of the second ring gear 11 becomes {j(k+1)Nr1+(k−j)Ns}/{k(j+1)}.

When the rotation speed of the input shaft 2 to which the cam disk 5 is fixed is the same as the rotation speed of the pinion shaft 7 , the rotary disk 6 rotates integrally with the cam disk 5 . When there is a difference between the rotation speed of the input shaft 2 and the rotation speed of the pinion shaft 7 , the rotating disk 6 rotates around the periphery of the cam disk 5 around the center point P2 of the cam disk 5 .

As shown in Figure 2, since the rotating disk 6 is eccentric relative to the cam disk 5, and the distance Ra is the same as the distance Rb, the center point P3 of the rotating disk 6 can be located on the same axis as the rotation center axis P1, so that the rotation center The distance between the axis P1 and the center point P3, that is, the eccentricity R1 is "0".

One end of the connecting rod 15 has an input-side annular portion 15a (input-side end) having a large diameter, and the other end has an output-side annular portion 15b (output-side end) having a diameter smaller than that of the input-side annular portion 15a. ), the input-side annular portion 15a of the connecting rod 15 is rotatably fitted on the periphery of the rotating disk 6 via the roller bearing 16 . Six swing links 18 are provided on the output shaft 3 corresponding to the connecting rod 15 via a one-way clutch 17 (one-way rotation preventing mechanism) as a one-way rotation preventing mechanism.

The swing link 18 has: an annular portion 18e on which the output shaft 3 is arranged on the inner peripheral side; link. A pair of protruding protrusions 18b are provided on the swing end portion 18a, and the protrusions 18b sandwich the output-side annular portion 15b in the axial direction. A through-hole 18c corresponding to the inner diameter of the output-side annular portion 15b is drilled in the pair of protruding pieces 18b. A cylindrical coupling pin 19 is inserted into the through hole 18c and the output-side annular portion 15b. Thus, the connecting rod 15 is connected to the swing link 18 . In addition, the connecting pin 19 is not limited to a cylindrical shape, and may be formed in a cylindrical shape. Here, the cylindrical shape includes a shape in which a circle is formed on the outer periphery thereof, and a circle or a polygon is formed on the inner periphery thereof.

3A to 3D show the positional relationship between the pinion shaft 7 and the rotating disk 6 in a state where the eccentricity R1 of the rotation radius adjusting mechanism 4 is changed. Fig. 3A shows the state where the eccentricity R1 is "maximum", the pinion shaft 7 and the rotating disk 6 are located so that the rotation center axis P1, the center point P2 of the cam disk 5, and the center point P3 of the rotating disk 6 are arranged on a straight line s position. At this time, the gear ratio i is the smallest.

FIG. 3B shows a state in which the eccentricity R1 is set to be "medium" smaller than that in Fig. 3A , and Fig. 3C shows a state in which the eccentricity R1 is set to "small" which is smaller than that in Fig. 3B . The gear ratio i in FIG. 3B is "medium", which is larger than the gear ratio i in FIG. 3A, and is "large" in FIG. 3C, which is higher than the gear ratio i in FIG. 3B.

FIG. 3D shows a state in which the eccentricity R1 is set to "0", and the rotation center axis P1 is concentric with the center point P3 of the rotary disk 6 . The gear ratio i at this time becomes infinite (∞).

As shown in FIG. 2 , the radius of rotation adjustment mechanism 4 , the connecting rod 15 , and the swing link 18 of the present embodiment constitute a four-bar mechanism type crank-link mechanism 20 . The continuously variable transmission 1 of the present embodiment has a total of six crank-link mechanisms 20 . When the eccentricity R1 is not "0", when the input shaft 2 is rotated and the pinion shaft 7 is rotated at the same speed as the input shaft 2, each connecting rod 15 changes its phase by 60 degrees at a time, while the phase is changed according to the eccentricity R1. , Between the input shaft 2 and the output shaft 3, alternately push to the side of the output shaft 3 and pull to the side of the input shaft 2, and repeat the alternating motion.

The output-side annular portion 15 b of the connecting rod 15 is connected to a swing link 18 provided on the output shaft 3 via a one-way clutch 17 , and the swing link 18 is pushed and pulled by rotation of the connecting rod 15 to swing. When the swing link 18 rotates to either side of the push direction and the pull direction, the output shaft 3 rotates, and when the swing link 18 rotates to the other side, the force of the swing movement of the swing link 18 is not transmitted to the output shaft. 3. The swing connecting rod 18 runs idle. Since the radius of rotation adjustment mechanisms 4 are arranged with a phase difference of 60 degrees, the output shaft 3 is rotated sequentially by the radius of rotation adjustment mechanisms 4 .

Fig. 4A shows that when the eccentricity R1 is "maximum" in Fig. 3A (when the transmission ratio i is the minimum), the swing range θ2 of the swing link 18 relative to the rotational movement of the radius of rotation adjustment mechanism 4, and Fig. 4B shows the eccentricity The amount R1 is the swing range θ2 of the rotary motion of the swing link 18 relative to the radius of rotation adjustment mechanism 4 during the "middle" of Fig. 3B (when the gear ratio i is middle), and Fig. 4C shows that the eccentricity R1 is shown in Fig. 3C The swing range θ2 of the swing link 18 relative to the rotation radius adjustment mechanism 4 when the "small" (speed ratio i is large).

It can be seen from FIG. 4A to FIG. 4C that as the eccentricity R1 becomes smaller, the swing range θ2 of the swing link 18 becomes narrower. In addition, when the eccentricity R1 is "0", the swing link 18 does not swing. In addition, in this embodiment, the position closest to the input shaft 2 within the swing range θ2 of the swing end portion 18a of the swing link 18 is defined as an inner dead point, and the position farthest from the input shaft 2 is defined as an outer dead point. .

Next, as shown in FIG. 5 and FIG. 6 , the continuously variable transmission 1 of the present embodiment has a connecting pin detachment prevention mechanism that restricts the connection pin 19 relative to the output side ring of the connecting rod 15 in the axial direction. The shape part 15b moves. Here, the axis direction is formed parallel to the direction in which the rotation center axis P1 extends.

The connecting pin detachment preventing mechanism is composed of the following structures: a groove portion 19a, which is provided on the outer peripheral surface of the connecting pin 19 so as to extend in a direction perpendicular to the axial direction; a hole portion 15c, which corresponds to the groove portion 19a in the axial direction. is provided on the output side annular portion 15b of the connecting rod 15 so as to extend in a direction perpendicular to the axial direction, and;

In this embodiment, the groove portion 19 a is formed on the entire circumference of the outer circumference of the coupling pin 19 . In addition, the length of the extending direction of the groove part 19a can also be set suitably according to the swing range of the swing link 18. As shown in FIG. Moreover, the groove part 19a is provided in the center position of the connection pin 19 in the axial direction.

In the present embodiment, the hole 15c of the output-side annular portion 15b of the connecting rod 15 is formed to have a circular cross-section, and is formed from the side of the annular portion 18e of the swing link 18 on the outer peripheral surface of the output-side annular portion 15b. The opening of the hole 15c extends toward the inside and cuts off a part of the inner peripheral surface of the output side annular portion 15b, and the end of the hole portion 15c is closed between the outer peripheral surface and the inner peripheral surface of the output side annular portion 15b. In addition, the cross section of the hole portion 15c is not limited to a circle, and may be a polygon.

As shown in FIGS. 2 and 4 , when the swing link 18 rotates in the push direction (direction away from the input shaft), the one-way clutch 17 transmits the force of the swing movement of the swing link 18 to the output shaft 3 .

Therefore, in the output-side annular portion 15b of the connecting rod 15 connected to the swing end portion 18a of the swing link 18, the left side of the connecting pin 19 (that is, the position closer to the input shaft 2 than the center of the connecting pin 19) ), a relatively low pressure is generated on the right side of the coupling pin 19 of the output-side annular portion 15b (that is, at a position farther from the input shaft 2 than the center of the coupling pin 19).

Therefore, in the present embodiment, the hole 15 c is provided at a position farther from the input shaft 2 than the center of the connecting pin 19 , and the reduction in the durability of the connecting rod 15 due to the hole 15 c is suppressed.

In addition, in the one-way clutch 17 of the present embodiment, when the swing link 18 rotates in the push direction (direction away from the input shaft), force is transmitted to the output shaft 3, so the formation position of the hole portion 15c is positioned opposite to each other. The lower pressure side (that is, the position farther from the input shaft 2 than the center of the connecting pin 19).

However, the present invention is not limited to such a structure. For example, when a one-way clutch is used that transmits force to the output shaft when the swing link rotates in the pulling direction (direction close to the input shaft), the position where relatively low pressure is generated is the opposite side of the present embodiment. Therefore, in this case, the hole is preferably positioned closer to the input shaft than the center of the connecting pin.

In this embodiment, the cross section of the anti-loosening pin 21 is circular, and the anti-loosening pin 21 extends along a straight line. The outer diameter of the drop-out preventing pin 21 is formed to be the same as the diameter of the hole portion 15c. Therefore, the output-side annular portion 15b and the drop-out prevention pin 21 do not move relative to each other in the axial direction.

In addition, the anti-dropout pin 21 is not limited to a circular shape in cross-sectional view, and may be formed in a polygonal shape such as a triangle or a quadrangle. In addition, the diameter of the drop-out preventing pin 21 and the diameter of the hole portion 15c do not necessarily have to be the same. For example, the diameter of the anti-dropping pin 21 may be slightly larger than that of the hole portion 15c, and it may be fixed by press-fitting. In addition, it is also possible to form the external thread on the anti-dropout pin 21 and the internal thread on the hole portion 15c, and screw them together to fix them.

The drop-out preventing pin 21 is formed so that a part thereof abuts against the inner surface of the groove portion 19a in a state inserted into the hole portion 15c. Accordingly, movement of the coupling pin 19 in the axial direction relative to the output-side annular portion 15 b can be restricted via the drop-out prevention pin 21 . At this time, the output-side annular portion 15b is rotatable about the axis with respect to the coupling pin 19 .

And, as shown in FIG. 5 , with regard to the drop-out preventing pin 21 inserted into the hole 15c of the output side annular portion 15b of the connecting rod 15, a part of its circumferential surface (arc portion) is in contact with the inside of the groove 19a of the connecting pin 19. The surface is in contact, and the other part of the peripheral surface is in contact with the inner peripheral surface of the hole 15c. Thereby, the output side annular part 15b and the connection pin 19 are prevented from moving relative to each other in the axial direction via the drop-out prevention pin 21 .

In addition, as shown in FIG. 7 , the drop-out prevention pin 21 is fixed to the output-side annular portion 15 b by adhesion or caulking in a state inserted from one end of the hole 15 c to the other end of the hole 15 c.

As shown in FIGS. 8A and 8B , even if the anti-dropping pin 21 moves along the extending direction of the hole 15c, the end of the anti-dropping pin 21 abuts against the outer peripheral surface 18f of the annular portion 18e of the swing link 18, and the anti-dropping pin 21 A part of it is still in contact with the inner surface of the groove portion 19a. Therefore, movement of the coupling pin 19 relative to the output-side annular portion 15b of the connecting rod 15 in the axial direction thereof can be restricted.

In addition, in this embodiment, the hole portion 15c is a blind hole, and when the swing angle of the swing link 18 is in the swing range (for example, the case of FIG. 8. In addition, FIG. 7 is a state in the production stage.), the hole The portion 15 c is formed such that the opening is located on the outer peripheral surface side of the annular portion 18 e of the swing link 18 . Therefore, even when the swing angle of the swing link 18 becomes maximum (even when the swing link 18 is located at the outer dead point or the inner dead point), the one end 21a of the anti-dropping pin 21 is in contact with the outer peripheral surface of the annular portion 18e of the swing link 18. 18f abutment.

However, the hole portion 15c does not necessarily have to be formed in this way, and may be formed as a through hole instead of a blind hole. In this case, in order to prevent the anti-dropping pin 21 from moving away from the swing link 18, for example, the swing end portion 18a of the swing link 18 may be configured to be located above the annular portion 18e.

As described above, in the continuously variable transmission 1 of the present embodiment, there is a connecting pin detachment prevention mechanism that restricts the movement of the connecting pin 19 relative to the output side annular portion 15b of the connecting rod 15 in the axial direction. . In addition, the connection pin detachment prevention mechanism is configured such that a part of the detachment prevention pin 21 inserted into the hole 15c provided on the output side annular portion 15b of the connecting rod 15 and the groove portion 19a provided on the outer peripheral surface of the connection pin 19 are connected. abutting inner surfaces.

That is, in the connecting pin detachment prevention mechanism of this embodiment, a part of the detachment prevention pin 21 inserted into the hole 15c provided on the output side annular portion 15b of the connecting rod 15 and the outer peripheral surface of the connection pin 19 are connected to each other. The inner surface of the groove portion 19a of the connecting pin 19 is abutted against to prevent movement (falling off) of the connecting pin 19 in the axial direction.

Therefore, in the continuously variable transmission 1 of the present embodiment, it is not necessary to shorten the connecting pin to arrange the annular member as the connecting pin detachment preventing mechanism. The space of the component and the amount of space forming the groove for fitting the ring-shaped component.

Therefore, according to the continuously variable transmission 1 of the present embodiment, when the swing link 18 is swung, substantially the entire inner circumference of the hole of the output side annular portion 15 b of the connecting rod 15 or the swing end portion 18 a of the swing link 18 can be moved. The surface is used as the effective surface under pressure.

In addition, since it is not a structure in which the anti-dropping member is arranged in contact with the end surface of the connecting pin 19, but one anti-dropping pin 21 is engaged with the connecting pin 19, one anti-dropping member may be used. . Thereby, the simplification of the connection pin detachment preventing mechanism can be realized.

Claims (4)

1. a stepless speed variator, described stepless speed variator has:

Input shaft;

Output shaft, itself and described input shaft configure abreast;

Connecting rod, it has turning radius controlling mechanism, swing connecting bar and connecting rod, described turning radius controlling mechanism comprises rotary part rotatable centered by the rotating center axis of described input shaft, and freely can regulate the turning radius of described rotary part, described swing connecting bar rotatably axle is supported on described output shaft and is provided with the swing end of ring-type, the outlet side end of ring-type that described connecting rod comprises the input side end that is rotatably connected with described rotary part and links with described swing end, the rotary motion of described input shaft is converted to the oscillating motion of described swing connecting bar by described connecting rod,

Single direction rotation stops mechanism, described swing connecting bar will be fixed relative to described output shaft to during a sideway swivel relative to described output shaft centered by the rotating center axis of described output shaft in described swing connecting bar by it, when described swing connecting bar will rotate to opposite side, described swing connecting bar is dallied relative to described output shaft; And

Cylindric or cylindric connection pin, the described swing end of described swing connecting bar and the described outlet side end of described connecting rod are run through in its rotating center axis direction along described output shaft, and described swing end is connected to can relatively rotate with described outlet side end

This stepless speed variator makes gear ratio change by making the turning radius of described rotary part change,

The feature of described stepless speed variator is,

Described stepless speed variator has connection pin escapement, and on the axial direction that this connection pin escapement is limited in described connection pin, described connection pin moves relative to the described outlet side end of described connecting rod,

Described connection pin escapement is formed by with lower part: groove portion, and it is arranged at the outer circumferential face of described connection pin in the mode extended along the direction orthogonal with the axial direction of described connection pin; Hole portion, it is arranged at the described outlet side end of described connecting rod in the mode that the position corresponding with described groove portion on the axial direction of described connection pin extends along the direction orthogonal with the axial direction of described connection pin; And locking pin, it is inserted in the portion of described hole,

Described locking pin abuts with the internal surface in described groove portion being inserted under the state in the portion of described hole.

2. stepless speed variator according to claim 1, is characterized in that,

Described swing connecting bar has annulus, configures described output shaft in the inner circumferential side of described annulus, and the outer circumferential face of described annulus is provided with described swing end,

Even if when described locking pin to move to described locking pin one end along described hole portion abuts with the outer circumferential face of described annulus, described locking pin also abuts with the internal surface in described groove portion.

3. stepless speed variator according to claim 1 and 2, is characterized in that,

When described swing connecting bar will rotate away from the mode of described input shaft with described swing end centered by the rotating center axis of described output shaft, described single direction rotation stops mechanism described swing connecting bar to be fixed relative to described output shaft, when described swing connecting bar will rotate close to the mode of described input shaft with described swing end, described single direction rotation stops mechanism that described swing connecting bar is dallied relative to described output shaft

Described hole portion is arranged on center than described connection pin from the position away from described input shaft.

4. stepless speed variator according to claim 1 and 2, is characterized in that,

When described swing connecting bar will rotate close to the mode of described input shaft with described swing end centered by the rotating center axis of described output shaft, described single direction rotation stops mechanism described swing connecting bar to be fixed relative to described output shaft, when described swing connecting bar will rotate away from the mode of described input shaft with described swing end, described single direction rotation stops mechanism that described swing connecting bar is dallied relative to described output shaft

Described hole portion is arranged on center than described connection pin from the position close to described input shaft.