JP2012067844A - Continuously variable transmission mechanism - Google Patents

Abstract

PROBLEM TO BE SOLVED: To easily store spring means between a center boss and movable teeth, by allowing the spring means biasing the movable teeth on the center boss in a radially outward direction to generate strong spring force with few strokes.SOLUTION: The spring means 19 biasing the movable teeth 17 in a radially outward direction within movable tooth holders 18 on the center boss 16 include an alternately continuous body constituted of U-shaped elements 21 for the movable tooth 17 and connecting elements 22 for connecting the adjacent legs 21a of the adjacent U-shaped elements 21. The connecting elements 22 are seated on the center boss 16, and the ends of the U-shaped elements 21 are seated on the movable tooth 17 with the U-shaped elements 21 extended toward the movable tooth 17. Accordingly, the spring means 19 are formed as a torsion spring type biasing the movable tooth 17 in the radially outward direction with the torsional reaction force of the connecting elements 22, and generate the strong spring force with few spring strokes.

Description

  The present invention comprises an endless chain link and a pulley around which the endless chain link is wound so as to be continuously variable, and is urged radially outward by a spring means around the outer periphery of the central boss of the pulley. The present invention relates to a continuously variable transmission mechanism capable of preventing slipping at a transmission ratio capable of meshing by meshing between a movable tooth provided so as to be able to advance and retract and a movable tooth meshing groove provided on an endless chain link. .

As this type of continuously variable transmission mechanism, a V-belt type continuously variable transmission is well known, and the endless chain link is stretched over the V groove of the pulley to enable power transmission,
By continuously changing the winding diameter of the endless chain link with respect to the pulley by changing the groove width of the pulley V groove during the power transmission, the continuously variable transmission can be performed.

On the other hand, as a technique for increasing the transmission efficiency by suppressing the slip of the continuously variable transmission mechanism, conventionally, as described in Patent Document 1, for example, teeth are projected on the outer peripheral surface of the central boss portion of the pulley that defines the bottom surface of the pulley V groove. Set up
While the tooth groove formed on the inner periphery of the endless chain link is in the transmission ratio that meshes with the teeth on the outer peripheral surface of the pulley center boss, the transmission efficiency of the continuously variable transmission mechanism is prevented by preventing slippage between the pulley and the endless chain link. A technique for improving the above has been proposed.

  On the other hand, in Patent Document 1, the teeth provided on the outer peripheral surface of the pulley central boss portion are configured as movable teeth that are urged radially outward by a spring means so as to be able to advance and retract in the radial direction. There has also been proposed a technique capable of preventing slippage at a transmission ratio meshed with a movable tooth meshing groove provided in a chain link.

According to this proposed technique, when the above-mentioned movable tooth fails to mesh with the inner peripheral tooth groove of the endless chain link, it can be retracted radially inward by the inner periphery of the endless chain link.
Since the teeth on the outer periphery of the pulley central boss part do not damage the endless chain link due to interference with the endless chain link, this is advantageous in terms of durability.

JP 2010-014269 A

  However, in the above-mentioned proposed technique, since the coil spring or the annular spring is used as the spring means for urging the movable tooth provided on the outer peripheral surface of the pulley center boss portion in the radial direction, the following problems are caused. Is produced.

When a coil spring is used as the spring means, the stroke of the coil spring required to generate the radially outward biasing force required by the movable tooth is large, and the coil spring is between the outer peripheral surface of the pulley center boss and the movable tooth. Is difficult to store.
However, when using a coil spring that fits in a space that can be secured between the outer peripheral surface of the pulley center boss and the movable tooth, it is difficult to generate the required spring force, and the movable tooth is required. Cannot be urged outward in the radial direction by the applied force.

  In order to earn a coil spring stroke, there is a method of reducing the shaft diameter of the pulley center boss, but this method has a problem in terms of durability due to insufficient shaft strength of the pulley center boss. .

On the other hand, when an annular spring is used as the spring means, a groove for escaping the annular spring is indispensable for the movable tooth, and the structure of the movable tooth becomes complicated and the cost increases.
After assembling the movable teeth first, the annular spring is assembled while being pressed against the movable teeth, and an elastic force is applied to the movable teeth, resulting in a problem that the workability of assembling the annular spring is poor.

  The present invention is a unique spring that does not cause the above-mentioned problem as a spring means for urging the movable teeth on the outer periphery of the pulley central boss portion radially outward, unlike a conventional coil spring or annular spring. It is an object of the present invention to provide a continuously variable transmission mechanism that can solve the above-described problems by using means.

For this purpose, the continuously variable transmission mechanism according to the present invention is constituted as follows.
First, in order to explain the continuously variable transmission mechanism that is the basic premise of the gist configuration of the present invention,
It consists of an endless chain link and a pulley wrapped around this endless chain link so that it can be continuously variable,
Engagement is achieved by meshing a movable tooth provided on the outer periphery of the central boss of the pulley so as to be able to advance and retreat in the radial direction by a spring means and a movable tooth meshing groove provided on the endless chain link. It is possible to prevent slip at a transmission ratio that can be

In the present invention, the spring means in the continuously variable transmission mechanism is particularly as follows.
That is, the spring means includes a U-shaped element interposed between the outer periphery of the central boss portion and the movable tooth so as to extend in the generatrix direction of the outer periphery of the central boss portion.
These U-shaped elements are oriented so that the opposing leg portions of the U-shaped element are seated on the outer periphery of the central boss portion at the mutual non-bonding ends, and the opposing leg portions are seated on the movable teeth at the mutual coupling ends. .

  Further, the adjacent leg portions of the adjacent U-shaped elements are joined to each other by connecting elements at the non-bonding ends so that the U-shaped elements are integrated with each other so that the U-shaped elements face each other. The leg is configured to apply a radially outward biasing force to the movable tooth at the mutual coupling end.

In such a continuously variable transmission mechanism of the present invention, the U-shaped element for each movable tooth is formed by connecting the U-shaped elements adjacent to each other by a connecting element as described above. In order to use the integrated unit as a spring means for movable teeth,
This spring means is a continuous body of a U-shaped element and a connecting element and becomes a torsion spring type spring means, and a large spring force can be generated with a relatively small spring stroke.

  Therefore, according to the present invention, it is possible to generate the radially outward biasing force required by the movable tooth with a small spring stroke, and even in a limited space between the pulley center boss outer periphery and the movable tooth, The spring means can be easily accommodated and the movable teeth can be urged radially outward with a predetermined force.

  Further, according to the present invention, since the required spring force can be generated with a small spring stroke as described above, it is not necessary to earn the spring stroke, and the shaft diameter of the pulley central boss portion needs to be reduced for the spring stroke. In addition, there is no problem of durability due to insufficient axial strength of the pulley center boss.

Further, according to the present invention, since the spring means is a continuous body of the U-shaped element and the connecting element, it is not necessary to provide the movable tooth with a groove for escaping these elements, and the structure of the movable tooth becomes complicated. There is no problem of high costs.
For the same reason, that is, since the spring means is a continuous body of the U-shaped element and the connecting element, this spring means can be assembled before the movable teeth are assembled to the outer periphery of the pulley center boss part, This is also very advantageous in terms of assembly workability.

1 is a schematic side view of a continuously variable transmission mechanism according to a first embodiment of the present invention. FIG. 2 is a detailed view showing a slip prevention mechanism of a winding transmission portion on the secondary pulley side of the continuously variable transmission mechanism shown in FIG. FIG. 3 is a detailed explanatory view showing an engagement state of a slip prevention mechanism between an endless chain link and a secondary pulley of the continuously variable transmission mechanism shown in FIGS. FIG. 4 is a perspective view showing a secondary pulley center boss portion of the continuously variable transmission mechanism shown in FIGS. 1 to 3 in a state where a movable tooth biasing spring means is attached, but before the movable teeth are attached. The secondary pulley center boss part shown in FIG. 4 is shown in a movable tooth attached state, (a) is a plan view showing a state where some movable teeth are attached to the secondary pulley center boss part, (b) is a secondary tooth It is a principal part vertical side view of a pulley center boss | hub part. The secondary pulley center boss part shown in FIG. 4 is shown in a movable tooth attached state, (a) is a perspective view showing a state in which all the movable teeth are attached to the secondary pulley center boss part, and (b) is a secondary pulley. FIG. 5 is a perspective view showing a part of a movable tooth biasing spring means by removing two movable teeth from a central boss portion. The movable pulley attached state of the secondary pulley central boss part is shown, (a) is a side view seen in the direction of arrow VII in FIG. 5 (a), (b) is an enlarged detail partial side view of the VIIb part in (a) (C) is an enlarged detail partial side view of the VIIc part in (a). 8 shows a movable tooth biasing spring means used in the continuously variable transmission mechanism of FIGS. 1 to 7, wherein (a) is an overall perspective view of the spring means, and (b) is the same spring relating to the VIII portion of (a). It is a partially enlarged detail perspective view of the means. FIG. 9 is an overall side view of the movable tooth biasing spring means shown in FIG. The characteristics of load change with respect to the spring stroke of the movable tooth biasing spring means shown in FIGS. 8 and 9 are compared with the load change characteristics of the movable tooth biasing spring means used in the conventional continuously variable transmission mechanism. FIG. The secondary pulley central boss part of the continuously variable transmission mechanism according to the second embodiment of the present invention is shown with a movable tooth attached state, (a) is a movable tooth by removing two movable teeth from the secondary pulley central boss part. FIG. 4B is a perspective view showing a part of the urging spring means, and FIG. FIG. 9 is an overall perspective view showing a movable tooth biasing spring means used in a continuously variable transmission mechanism according to a third embodiment of the present invention. FIG. 7 is a perspective view showing a secondary pulley central boss portion of a continuously variable transmission mechanism according to a third embodiment in a state where a movable tooth biasing spring means is attached but before a movable tooth is attached. The secondary pulley center boss part shown in FIG. 13 is shown in a movable tooth attached state, (a) is a plan view showing a state where some movable teeth are attached to the secondary pulley center boss part, (b) is a secondary tooth It is a principal part vertical side view of a pulley center boss | hub part. The secondary pulley center boss portion shown in FIG. 13 is shown with a movable tooth attached state, (a) is a perspective view showing a state where all the movable teeth are attached to the secondary pulley center boss portion, (b) is a secondary pulley. FIG. 5 is a perspective view showing a part of a movable tooth biasing spring means by removing two movable teeth from a central boss portion.

Hereinafter, embodiments of the present invention will be described in detail based on examples shown in the drawings.
<Configuration of the first embodiment>
1 to 10 show a continuously variable transmission mechanism according to a first embodiment of the present invention, FIG. 1 is a schematic side view of the continuously variable transmission mechanism 10, and FIG. 2 is a winding transmission on the secondary pulley side. FIG.

In FIG. 1, 11 is a primary pulley that is a driving pulley of the continuously variable transmission mechanism 10, and 12 is a secondary pulley that is a driven pulley.
An endless chain link 13 is provided between the primary pulley 11 and the secondary pulley 12, and
The continuously variable transmission mechanism 10 can transmit power between the primary pulley 11 and the secondary pulley 12 via the endless chain link 13.

  Each of the primary pulley 11 and the secondary pulley 12 has opposed sheaves 11a and 12a that face each other in the rotation axis direction (in FIG. 1, for convenience, the front sheave is removed and only the sheave on the other side is shown). A V-groove pulley having a pulley V-groove defined between 11a and the opposing sheave 12a.

As clearly shown in FIG. 2, the endless chain link 13 is formed in a continuous annular shape by connecting a large number of link plates 14 in a chain shape with link pins 15 in link pin insertion holes 14a at both ends.
Both end surfaces of each link pin 15 are inclined so as to come into surface contact with the inner side surface of the opposed sheave 11a and the inner side surface of the opposed sheave 12a that provide the pulley V groove side walls of the primary pulley 11 and the secondary pulley 12.

  Thus, the endless chain link 13 is clamped between the opposed sheave 11a of the primary pulley 11 and the opposed sheave 12a of the secondary pulley 12 in the region where the pulley is wound, and between the primary pulley 11 and the secondary pulley 12. Power transmission can be performed.

One of the opposed sheaves 11a of the primary pulley 11 is a fixed sheave, and the other is a movable sheave capable of stroke control in the axial direction.
The facing sheave 12a of the secondary pulley 12 has a sheave on the same side as the movable sheave of the primary pulley 11 as a fixed sheave, and a sheave on the same side as the fixed sheave of the primary pulley 11 as a movable sheave capable of stroke control in the axial direction.

As the movable sheave of the primary pulley 11 approaches the fixed sheave to narrow the pulley V groove width, the movable sheave of the secondary pulley 12 is moved away from the fixed sheave to widen the pulley V groove width.
The endless chain link 13 has an increased winding diameter with respect to the primary pulley 11 and a reduced winding diameter with respect to the secondary pulley 12, and the continuously variable transmission mechanism 10 moves toward the highest gear ratio selection state shown in FIG. It can be increased under infinitely variable speed.

Conversely, as the movable sheave of the primary pulley 11 is moved away from the fixed sheave to increase the pulley V groove width, the movable sheave of the secondary pulley 12 is brought closer to the fixed sheave to narrow the pulley V groove width.
The endless chain link 13 has a reduced winding diameter with respect to the primary pulley 11 and an increased winding diameter with respect to the secondary pulley 12, and the continuously variable transmission mechanism 10 is shown in the state from the highest gear ratio selection state shown in FIG. It is possible to downshift under a continuously variable transmission toward a lowest gear ratio selection state not shown.

In order to improve the transmission efficiency of the continuously variable transmission mechanism 10 by suppressing the slip of the endless chain link 13 with respect to the secondary pulley 12 in the above-described highest gear ratio selection state of FIG. A plurality of movable teeth 17 are provided on the central boss portion 16 at regular intervals in the circumferential direction so as to protrude from the outer peripheral surface thereof.
These movable teeth 17 are fitted to a cylindrical movable tooth holder 18 fitted to the outer peripheral surface of the secondary pulley central boss portion 16 so as to be able to advance and retract in the radial direction within a limited range, and spring means as will be described in detail later. As shown in FIGS. 1 and 2, it is elastically supported by the advance limit position projecting radially outward from the movable tooth holder 18 as shown in FIGS.

Movable teeth meshing with the inner edge of each link plate 14 defining the inner peripheral edge of the endless chain link 13 so that the protruding tip of the movable tooth 17 meshes as shown in FIGS. Providing a groove 14b,
By engaging the movable tooth 17 and the movable tooth meshing groove 14b, it is possible to suppress the slip of the endless chain link 13 with respect to the secondary pulley 12 in the highest gear ratio selection state, and to improve the transmission efficiency of the continuously variable transmission mechanism 10. it can.

  Therefore, when the movable tooth 17 is not aligned with the movable tooth meshing groove 14b and cannot be meshed with the movable tooth meshing groove 14b, the movable tooth 17 is pushed back into the movable tooth holder 18 by the inner edge of the link plate 14 against the spring means 19. The position of the movable tooth 17 can be prevented from being damaged by interference with the endless chain link 13.

<Details of spring means>
In this embodiment, a set of three spring means 19 for urging the movable teeth 17 in the movable tooth holder 18 outward in the radial direction on the outer periphery of the secondary pulley central boss portion 16 as shown in FIGS. These spring means 19 are distributed in the longitudinal direction of the movable teeth 17, that is, in the axial direction of the secondary pulley central boss portion 16.
In this distributed arrangement, it is preferable to disperse the spring means 19 so that the movable teeth 17 are equally divided in the longitudinal direction as much as possible.

All of the spring means 19 are the same, and have the following configuration described with reference to FIGS.
As shown in FIGS. 8 (a) and 9 as a whole, the spring means 19 in this embodiment has a linear U-shaped element 21 and a linear linear connecting element 22 alternately in the same circle. Arrange on the circumference to make an integrated unit.

The U-shaped element 21 is located between the outer periphery of the secondary pulley central boss portion 16 and each movable tooth 17, that is, in the corresponding movable tooth receiving groove 18a of the movable tooth holder 18, toward the generatrix of the outer periphery of the central boss portion. Intervene to extend.
Therefore, there are as many U-shaped elements 21 as movable teeth 17, and these U-shaped elements 21 have their opposing leg portions 21a seated on the outer periphery of the secondary pulley central boss portion 16 at the mutual non-bonding ends. The portion 21a is oriented so as to be seated on the movable tooth 17 at the mutual coupling end, and the orientation direction of the U-shaped element 21 is made the same by the three spring means 19.

All the U-shaped elements 21 are integrated with each other by connecting the adjacent leg portions 21a of the adjacent U-shaped elements 21 to each other by the connecting elements 22 at their non-bonding ends.
When integrating these U-shaped elements 21, the U-shaped elements 21 are inclined by an angle indicated by θ in FIG. 9 so that the mutual coupling ends of the opposed leg portions 21a are closer to the movable teeth 17 than the mutual non-coupling ends. Thus, it is assumed that the U-shaped element 21 exists in the shape of a Belleville spring over the entire circumference.
Thus, the spring means 19 becomes a continuous linear body composed of an alternating combination of the linear elements 21 and 22, and has a torsion spring type structure.

By the way, the spring means 19 does not connect the adjacent leg portions 21a of the adjacent U-shaped elements 21 in the VIII portion of FIG. It is configured in a C shape with parts cut out.
Then, spring means spread prevention hooks 23 as shown in FIGS. 8 (a) and 8 (b) are provided on adjacent leg portions 21a of adjacent U-shaped elements 21 that are not connected to each other.

The above-mentioned C-shaped spring means 19 shown in FIGS. 8 and 9 are made into a set of three, and each is expanded in the circumferential direction at the notch VIII in FIGS. 8 (a) and (b). In the state, as shown in FIGS. 4, 5 (a), 5 (b), and 6 (b), the spring means 19 is fitted into the corresponding circumferential groove on the movable tooth holder 18.
At this time, the three C-shaped spring means 19 are rotated so that the notches provided with the spring means spread prevention hooks 23 are aligned with the movable teeth 17 at equal circumferential positions (120 °). In position, it fits into a corresponding circumferential groove on the movable tooth holder 18.

  And, at the time of this fitting, as shown in FIGS. 4 and 5 (a), the spring means spread prevention hook 23 is engaged with the corresponding step portion 18b on the movable tooth holder 18, thereby making a set of three C Each of the letter spring means 19 is prevented from expanding in the circumferential direction.

  After fitting the C-shaped spring means 19 into the corresponding circumferential groove on the movable tooth holder 18, the movable tooth 17 is inserted into the movable tooth receiving groove 18a on the movable tooth holder 18, and the movable tooth holder is inserted. The assembly of the spring means 19 and the movable tooth 17 to 18 is completed.

<Operational effects of the first embodiment>
The spring means 19 as described above is assembled by inserting the movable teeth 17 into the movable tooth receiving grooves 18a on the movable tooth holder 18 by appropriately setting the inclination angle θ of the U-shaped element 21 shown in FIG. At this time, the opposing leg 21a of the U-shaped element 21 is pushed inward in the radial direction by the movable teeth 17 at the mutual coupling ends, and the connecting element 22 is twisted and deformed.
Therefore, when the movable tooth 17 is assembled, the torsional deformation reaction force of the connecting element 22 urges the movable tooth 17 radially outward in the movable tooth receiving groove 18a of the movable tooth holder 18, and the movable tooth 17 is normally movable. It can be elastically supported at the advance limit position protruding radially outward from the movable tooth receiving groove 18a of the holder 18, and the above-described slip prevention can be realized.

By the way, in the present embodiment, the spring means 19 for elastically supporting the movable tooth 17 at this position is provided, in particular, between the U-shaped element 21 for each movable tooth 17 and the adjacent leg portion 21a of the adjacent U-shaped element 21. Because it is configured by an alternating continuous body with the connecting elements 22 that are coupled to each other,
As shown in FIG. 10, α2 (when the U-shaped element inclination angle θ is large) and α3 (when the U-shaped element inclination angle θ is small) as shown in FIG. A larger load (spring force) can be generated with a smaller spring stroke than the conventional characteristic α1 in the case of using.

  Therefore, the radial outward urging force required by the movable tooth 17 can be generated with a small spring stroke, and even in the limited space between the outer periphery of the pulley center boss part 16 and the movable tooth 17, The spring means 19 can be easily accommodated, and the movable tooth 17 can be urged radially outward with a predetermined force.

  Further, according to the spring means 19 of the present embodiment, since the required spring force can be generated with a small spring stroke as described above, there is no need to earn a spring stroke, and the pulley central boss portion 16 of the pulley center boss portion 16 is used for the spring stroke. There is no need to reduce the shaft diameter, and there is no problem of durability due to insufficient shaft strength of the pulley center boss portion 16.

Further, according to this embodiment, since the spring means 19 is a continuous body of the U-shaped element 21 and the connecting element 22, it is not necessary to provide a groove for escaping these elements 21 and 22 in the movable tooth 17, and the movable means 17 is movable. There is no problem that the structure of the tooth 17 is complicated and the cost is increased.
For the same reason, that is, since the spring means 19 is a continuous body of the U-shaped element 21 and the connecting element 22, the spring means 19 assembles the movable teeth 17 on the outer periphery of the pulley center boss portion 16 as described above. It can be assembled in advance, which is very advantageous in terms of assembly workability.

Further, a plurality of (three) spring means 19 as described above are made into a set, and these spring means 19 are dispersedly arranged in the axial direction of the central boss portion 16 so that the plurality (three) spring means 19 are U-shaped. Because the movable tooth 17 is urged radially outward at the longitudinally equalized portion via the character element 21,
Even when the movable tooth 17 is a long object, the movable tooth 17 can be urged radially outwardly with a good balance in the longitudinal direction, and the movable tooth 17 can be prevented from coming into contact with each other.

Further, among the adjacent U-shaped elements 21, a pair of adjacent U-shaped elements are configured by the spring means 19 in a C-shape without being coupled by the connecting elements 22 between the adjacent leg portions 21a.
With the spring means 19 expanded in the circumferential direction at the C-shaped notch, as shown in FIGS. 4, 5 (a), (b), and 6 (b), on the movable tooth holder 18 Can be fitted into the corresponding circumferential grooves, and the assembling work of the spring means 19 is easy.

Further, each of the adjacent leg portions 21a of the pair of adjacent U-shaped elements 21 not coupled by the connecting element 22 engages with the stepped portion 18b on the movable tooth holder 18, and the circle of the C-shaped spring means 19 is obtained. Because the expansion prevention hook 23 that prevents the expansion in the circumferential direction is provided,
The C-shaped spring means 19 can be prevented from being displaced in the circumferential direction by this expansion, and the U-shaped element 21 is centered with respect to the movable tooth 17 as shown in FIGS. 7 (b) and 7 (c). It is possible to further secure the above-mentioned effects by maintaining the stock state.

Further, when the three C-shaped spring means 19 are fitted into the corresponding circumferential grooves on the movable tooth holder 18, the C-shaped spring means 19 is cut at the location where the spring means expansion preventing hook 23 is installed. Because the notch is in a rotational position that aligns with the movable teeth 17 located at circumferentially equidistant positions (120 °), the fitting is performed.
Any of the C-shaped spring means 19 (U-shaped element 21) does not generate movable teeth 17 that are not urged radially outward, and the notches of the three C-shaped spring means 19 As a result of being equally distributed in the circumferential direction, the generation of the movable teeth 17 that are not urged outward in the radial direction due to the presence of the notches can be evenly distributed in the circumferential direction.

<Configuration of the second embodiment>
FIG. 11 shows a continuously variable transmission mechanism according to a second embodiment of the present invention. FIG. 11 (a) shows a state of the spring means 19 by removing a part of the movable teeth 17 as in FIG. 6 (b). The arrangement is clearly shown, and FIG. 5B is a longitudinal sectional side view of the main part of the continuously variable transmission mechanism.
In FIGS. 11 (a) and 11 (b), parts that function in the same way as in the first embodiment are denoted by the same reference numerals.

The spring means 19 is a C-shaped spring means similar to that in the first embodiment as shown in FIGS.
However, in the case of the present embodiment, two such spring means 19 are set as a set, and the two spring means 19 are arranged so that the connecting elements 22 are close to each other as shown in FIG. 8 (a) and 8 (b) in a state of being expanded in the circumferential direction, as shown in FIGS. 11 (a) and 11 (b), a corresponding circle on the movable tooth holder 18 is obtained. Fits into the circumferential groove.
At this time, the two C-shaped spring means 19 are in a rotational position such that the notch portion provided with the spring means expansion preventing hook 23 (see FIG. 8) is aligned with the movable tooth 17 at the diametrically opposed position. Then, it fits into the corresponding circumferential groove on the movable tooth holder 18.

  After fitting two sets of C-shaped spring means 19 into corresponding circumferential grooves on the movable tooth holder 18, the movable teeth 17 are inserted into the movable tooth receiving grooves 18a on the movable tooth holder 18. Thus, the assembly of the spring means 19 and the movable teeth 17 to the movable tooth holder 18 is completed.

When the movable teeth 17 are attached, the pair of C-shaped spring means 19 has a pair of opposite leg portions 21a of U-shaped elements 21 extending in a direction away from each other by the movable teeth 17 at the mutual coupling ends. The connecting element 22 is torsionally deformed by being pushed inward in the direction.
Therefore, when the movable tooth 17 is assembled, the torsional deformation reaction force of the connecting element 22 urges the movable tooth 17 radially outward in the movable tooth receiving groove 18a of the movable tooth holder 18, and the movable tooth 17 is normally movable. It can be elastically supported at the advance limit position protruding radially outward from the movable tooth receiving groove 18a of the holder 18, and the above-described slip prevention can be realized.

<Operational effects of the second embodiment>
Also in the second embodiment described above, the spring means 19 that elastically supports the movable tooth 17 at the advance limit position has the same torsion spring type configuration as in the first embodiment described above.
The spring means 19 can generate the radially outward biasing force required by the movable tooth 17 with a small spring stroke, and even in a limited space between the outer periphery of the pulley center boss portion 16 and the movable tooth 17, The spring means 19 can be easily housed here, and the effect of being able to bias the movable tooth 17 radially outward with a predetermined force can be achieved,
All of the various effects described above according to the other first embodiment can be achieved in the second embodiment as well.

Furthermore, since the spring means 19 as described above are made into a set of two, and these spring means 19 are arranged back to back where the connecting elements 22 are close to each other,
By arranging two sets of spring means 19 so as to be symmetric with respect to the central position in the longitudinal direction of the movable teeth 17, the set of two spring means 19 is connected to the movable teeth 17 via the U-shaped element 21. It can be urged radially outwards uniformly throughout the longitudinal direction,
Even when the movable tooth 17 is a long object, the movable tooth 17 can be urged radially outwardly with a good balance in the longitudinal direction, and the movable tooth 17 can be prevented from coming into contact with each other.

Further, when the set of two spring means 19 is fitted into the corresponding circumferential groove on the movable tooth holder 18, the spring means 19 is an installation location of the spring means expansion preventing hook 23 (see FIG. 8). Because the notch is in a rotational position that aligns with the movable part 17 at the diametrically opposed position, and the fitting is performed,
None of the spring means 19 (U-shaped element 21) generates the movable teeth 17 that are not urged radially outward, and the notches of the two C-shaped spring means 19 are circumferential. Therefore, the generation of the movable teeth 17 that are not biased radially outward due to the presence of the notch can be evenly distributed in the circumferential direction.

<Configuration of the third embodiment>
12 to 15 show a continuously variable transmission mechanism according to a third embodiment of the present invention. In this embodiment, three rows of spring means are distributed in the axial direction of the central boss portion 16 as in the first embodiment. Although the arrangement is followed, as a spring means of each row, as shown in FIG. 12, a set of spring means of two inner and outer peripheries comprising an inner peripheral side spring means 19i and an outer peripheral side spring means 19o is used.
12 to 15, parts that function in the same manner as in the first embodiment are indicated by the same reference numerals.

As shown in FIG. 12, the inner peripheral spring means 19i and the outer peripheral spring means 19o are basically C-shaped spring means similar to those in the first embodiment described above with reference to FIGS.
Each of the inner peripheral spring means 19i and the outer peripheral spring means 19o includes U-shaped elements 21i, 21o, connecting elements 22i, 22o, and spring means expansion preventing hooks 23i, 23o, respectively.

However, since the outer peripheral spring means 19o is arranged to overlap the inner peripheral spring means 19i in the radial direction, it is needless to say that the outer peripheral spring means 19o has a larger diameter than the inner peripheral spring means 19i.
Of the U-shaped element 21i and the connecting element 22i provided on the inner peripheral spring means 19i, the U-shaped element 21i has every other movable tooth 17 attached radially outward as shown in FIGS. It is assumed that it exists at a position aligned with every other movable tooth 17 so as to be biased, and the connecting element 22i is connected to each other in the same manner as described above between the U-shaped elements 21i.

  Furthermore, of the U-shaped element 21o and the connecting element 22o provided on the outer peripheral side spring means 19o, the U-shaped element 21o attaches the remaining movable teeth 17 radially outward as shown in FIGS. It is assumed that it exists in a position aligned with the remaining every other movable tooth 17 so as to be biased, and the connecting element 22o is to interconnect the U-shaped elements 21o in the same manner as described above. .

In assembling the inner peripheral side spring means 19i and the outer peripheral side spring means 19o, first, the inner peripheral side spring means 19i is expanded in the circumferential direction at a notch portion where the spring means expansion preventing hook 23i is provided, In this state, as shown in FIGS. 13 to 15, the inner peripheral spring means 19 i is fitted into the corresponding circumferential groove on the movable tooth holder 18.
At this time, the inner row spring means 19i in the three rows are arranged such that the notches provided with the spring means spread prevention hooks 23i are aligned with the movable teeth 17 at circumferentially equidistant positions (120 °). In the rotational position, it fits into a corresponding circumferential groove on the movable tooth holder 18.

  And, at the time of this fitting, as shown in FIG. 13, the spring means expansion prevention hook 23i is engaged with the corresponding step portion 18b on the movable tooth holder 18, whereby the three rows of the inner peripheral side spring means 19i are respectively Prevents expansion in the circumferential direction.

Next, the outer peripheral spring means 19o is expanded in the circumferential direction at the notch where the spring means expansion preventing hook 23o is provided. In this state, as shown in FIGS. The side spring means 19i is placed over the corresponding circumferential groove on the movable tooth holder 18.
At this time, the outer spring means 19o has a notch where the spring means spread prevention hook 23o is provided at a position diametrically opposed to the notch of the inner spring 19i, and the U-shaped element 21o. Is engaged with the corresponding circumferential groove on the movable tooth holder 18 at a rotational position such that is located between the U-shaped elements 21i of the inner peripheral spring means 19i.
Further, the outer row spring means 19o in the three rows are each in a rotational position where the notches provided with the spring means spread prevention hooks 23o are aligned with the movable teeth 17 located at equal circumferential intervals (120 °). Thus, it fits into the corresponding circumferential groove on the movable tooth holder 18.

  At the time of this fitting, as shown in FIG. 14 (a), the spring means expansion prevention hook 23o is engaged with the corresponding step portion 18b on the movable tooth holder 18, so that the three rows of outer spring means 19o are arranged. Each is prevented from expanding in the circumferential direction.

  Thus, after the inner peripheral side spring means 19i and the outer peripheral side spring means 19o are fitted to the corresponding circumferential grooves on the movable tooth holder 18, the movable teeth 17 are placed in the movable tooth receiving grooves 18a on the movable tooth holder 18. 14 and 15, the assembly of the spring means 19i, 19o and the movable teeth 17 to the movable tooth holder 18 is completed.

  Thus, each pair of inner peripheral spring means 19i and outer peripheral spring means 19o urges the movable teeth 17 to move radially outward by the U-shaped elements 21i, 21o, and these movable teeth 17 are normally movable. It is possible to elastically support the advance limit position projecting radially outward from the movable tooth receiving groove 18a of the tooth holder 18, and the above-described slip prevention can be realized.

<Operational effects of the third embodiment>
Also in the third embodiment described above, the spring means 19i, 19o for elastically supporting the movable tooth 17 at the advance limit position has the same torsion spring type configuration as in the first embodiment described above.
The spring means 19i, 19o can generate the radially outward biasing force required by the movable tooth 17 with a small spring stroke, and the limited space between the outer periphery of the pulley center boss portion 16 and the movable tooth 17 However, the spring means 19i, 19o can be easily accommodated here, and the effect of being able to bias the movable teeth 17 radially outward with a predetermined force can be achieved.
All of the various effects described above according to the first embodiment can be similarly achieved in the third embodiment.

Further, according to the present embodiment, the spring means at the same axial position is composed of a pair of spring means 19i, 19o of the inner and outer peripheries, and these inner circumference side spring means 19i and outer circumference side spring means 19o (U-shaped element) 21i, 21o) in order to urge the movable teeth 17 alternately in the radial direction to elastically support the advance limit position,
The distance between the movable teeth 17 that the U-shaped element 21i of the inner peripheral spring means 19i urges radially outward is large, and the U-shaped element 21o of the outer spring means 19o urges radially outward. The interval between the movable teeth 17 is also large, and the tendency of affecting the adjacent movable teeth 17 can be alleviated.

For example, although one of the adjacent movable teeth 17 urged radially outward by the U-shaped element 21i meshes with the movable tooth meshing groove 14b of the endless chain link 13 (link plate 14), Even when the other side does not mesh with the movable tooth meshing groove 14b of the endless chain link 13 (link plate 14) and is pushed in due to interference with the endless chain link 13 (link plate 14),
In the present embodiment, since the distance between the adjacent movable teeth 17 is large, the tendency of affecting the adjacent movable teeth 17 can be alleviated and a stable load can be continuously applied to the movable teeth 17.

Further, the relative rotational positions of the inner peripheral spring means 19i and the outer peripheral spring means 19o are as described above, and the notch portion of the inner peripheral spring means 19i provided with the spring means expansion preventing hook 23i, Since the notch portion of the outer peripheral side spring means 19o provided with the spring means spread prevention hook 23o is in a position facing the diameter direction,
The movable teeth 17 that are not urged radially outward are not generated by any of the inner-side spring means 19i and the outer-side spring means 19o that make a pair, and the notches of the spring means 19i, 19o are circular. As a result of being equally distributed in the circumferential direction, the generation of the movable teeth 17 that are not urged outward in the radial direction due to the presence of the notches can be equally distributed in the circumferential direction.

<Other examples>
In the third embodiment shown in FIGS. 12 to 15, the springs in each row are arranged in the case where three rows of spring means are dispersedly arranged in the axial direction of the central boss portion 16 as in the first embodiment shown in FIGS. The means is constituted by a combination of the inner peripheral spring means 19i and the outer peripheral spring means 19o,
The present invention is not limited to this, and even when two rows of spring means are disposed in the opposite direction in the axial direction of the central boss portion 16 as in the second embodiment shown in FIG. According to the same concept as in the third embodiment, the inner peripheral side spring means 19i and the outer peripheral side spring means 19o can be combined to obtain the same effect.

10 Continuously variable transmission mechanism
11 Primary pulley
12 Secondary pulley
13 Endless chain link
14 Link plate
14a Link pin insertion hole
14b Movable tooth engagement groove
15 Link pin
16 Pulley center boss
17 movable teeth
18 Movable tooth holder
18a Movable tooth receiving groove
19 Spring means
19i Inner spring means
19o Outer spring means
21,21i, 21o U-shaped element
21a Opposing legs
22,22i, 22o Connecting element
23,23i, 23o Spring means expansion prevention hook

Claims (6)

It consists of an endless chain link and a pulley wrapped around this endless chain link so that it can be continuously variable,
Engagement is achieved by meshing a movable tooth provided on the outer periphery of the central boss of the pulley so as to be able to advance and retreat in the radial direction by a spring means and a movable tooth meshing groove provided on the endless chain link. In a continuously variable transmission mechanism that enables slip prevention at a transmission ratio capable of
The spring means comprises a U-shaped element interposed between the outer periphery of the central boss portion and the movable tooth so as to extend in the generatrix direction of the outer periphery of the central boss portion,
These U-shaped elements are oriented so that the opposing leg portions of the U-shaped element are seated on the outer periphery of the central boss portion at the mutual non-bonding ends, and the opposing leg portions are seated on the movable teeth at the mutual coupling ends,
The adjacent leg portions of the adjacent U-shaped elements are joined to each other by connecting elements at the non-bonding ends so that the U-shaped elements are integrated with each other, and the opposing leg portions of the U-shaped element are combined. Is a continuously variable transmission mechanism configured to apply a radially outward biasing force to the movable teeth at the mutual coupling ends. In the continuously variable transmission mechanism according to claim 1,
A continuously variable step, wherein the opposing leg portion of the U-shaped element applies a biasing force to the movable tooth at the mutual coupling end in the radial direction by a torsion spring reaction force of the connecting element. Variable speed transmission mechanism. In the continuously variable transmission mechanism according to claim 1 or 2,
Of the adjacent U-shaped elements, a pair of adjacent U-shaped elements are formed by integrating the U-shaped elements without connecting the adjacent legs by the connecting elements. A continuously variable transmission mechanism characterized in that the control unit is configured in a C shape. In the continuously variable transmission mechanism according to claim 3,
Enlarging the C-shaped integrated unit in the circumferential direction by engaging the outer periphery of the central boss portion with the adjacent leg portions of the pair of adjacent U-shaped elements that are not coupled by the connecting element. A continuously variable transmission mechanism characterized in that a spread prevention hook is provided to prevent this. In the continuously variable transmission mechanism according to any one of claims 1 to 4,
A continuously variable transmission mechanism comprising a plurality of U-shaped element mutual integrated units, and the U-shaped element mutually integrated units distributed in the axial direction of the central boss portion. In the continuously variable transmission mechanism according to any one of claims 1 to 5,
A plurality of U-shaped element mutual integrated units are provided as a set at the same axial position of the central boss portion, and these units are U-shaped elements that urge alternate movable teeth radially outward. A continuously variable transmission mechanism characterized by being set.

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