JP4789525B2 - Continuously variable transmission - Google Patents

Description

  The present invention relates to a continuously variable transmission, and more particularly, to an eccentric continuously variable transmission in which the center of a driven member is eccentric with respect to the center of a drive member.

Examples of the eccentric type continuously variable transmission include Patent Documents 1 and 2.
JP-A-6-74316 JP-A-9-303520

  Patent Document 1 has the following configuration. A rotationally driven outer peripheral gear is rotatably provided on the outer periphery of the cylindrical adjustment body, and a cylindrical body that penetrates the adjustment body at its eccentric position is rotatably supported between the bearings of the bearing device. . The bearing device is biased toward the input side and is configured to be rotatable in the biasing direction. An output shaft having a gear on the outer periphery is disposed in an axial direction inside the cylinder at a position eccentric from the axis of the cylinder, and is rotatably supported by the bearing device. In the cylindrical body, n windows having a circumferential length corresponding to the central angle (360 / n) ° are spirally formed one by one so as to be sequentially shifted in the circumferential direction and the axial direction. .

  In the cylindrical body, there are n divided parts having a ring-shaped inner periphery of the main body with partial teeth divided into n equal parts, and an outer periphery of the main body having a locking arm that is rotatable via an appropriate support. Each internal gear is inserted. The partial teeth are configured to mesh with the gear of the output shaft, and the support body and the locking arm protrude from the corresponding window with a gap in the circumferential direction, and are rotatable to the inner periphery of the outer peripheral gear. It is fixed to.

  Therefore, the following effects are exhibited. Each of the n divided internal gears inserted into the cylindrical body has partial teeth obtained by dividing the inner circumference into n parts, and they are arranged so that they are shifted one by one in the circumferential direction and in the axial direction. Therefore, a spiral inner peripheral gear is formed in the cylindrical body by all these n partial teeth. On the other hand, since the gear of the output shaft is in an eccentric position with respect to the cylindrical body, the gear of the output shaft meshes with a part of the inner peripheral gear, that is, any partial tooth of each divided internal gear. Accordingly, the path through which the rotation of the input shaft is transmitted to the output shaft is the gear of the input shaft, the outer peripheral gear, the locking arm, the support, the divided internal gear, and the output shaft.

  Therefore, the rotation of the outer peripheral gear is transmitted to each divided internal gear via the locking arm, but the cylindrical body (inner peripheral gear) is in an eccentric position with respect to the outer peripheral gear, and the support body and the locking arm. Projecting from the corresponding window with a gap in the circumferential direction, the rotational speed of the outer peripheral gear and the rotational speed of the inner peripheral gear coincide with each other, but the angular velocity differs depending on each divided internal gear. Therefore, due to the difference in angular velocity, a rotation different from the rotation of the outer peripheral gear is transmitted to the gear of the output shaft, and a shift is realized.

  In order to change the speed steplessly, the eccentric angle of the eccentric position of the cylindrical body may be continuously changed by appropriately rotating the adjustment body. In this case, the reaction force of the outer peripheral gear due to the eccentricity of the cylindrical body is compensated by the turning bias of the adjusting device. Note that the approach / separation between each divided internal gear and the inner periphery of the outer peripheral gear due to the eccentricity of the cylindrical body with respect to the outer peripheral gear is absorbed by the support and the locking arm.

  Patent Document 2 has the following configuration. A large gear rotated by an input shaft, an active ring connected to the inner peripheral side of the large gear by a link mechanism, a half-moon-shaped crescent bar that fits in the active ring and moves up and down by a lifting means, and the crescent An output shaft eccentrically inserted into the bar and rotatably supported by the lifting means; a driving claw member having a plurality of claw pieces provided on the circumference of the active ring as a unit; and the driving claw The member includes a driven-side claw member that engages with the outer periphery of the crescent bar and meshes with a plurality of claw pieces provided on the outer periphery of the output shaft that is inserted through the opening of the crescent bar. The driving claw member transmits rotational torque to the output shaft in the meshing section with the driven claw member.

  Therefore, the following effects are exhibited. When the large gear to be rotated on the input shaft rotates at a constant rotational speed, the rotational torque of the large gear is only when the driving-side claw member provided between the active ring and the output shaft meshes with the driven-side claw member. It is transmitted to the output shaft. At this time, if the axial center position of the active ring is deviated upward or downward with respect to the axial center position of the large gear, the peripheral speed on the active ring side at the meshing point of the driving side claw member and the driven side claw member. Is in a speed-up or speed-down relationship, and the output shaft is necessarily speeded up or slowed down.

  Each of the above prior arts has a complicated structure, a large number of components, and is expensive and large. In order to change the speed, it is necessary to change the interval between the input shaft and the output shaft, and it is very difficult to change this interval.

  SUMMARY OF THE INVENTION An object of the present invention is to provide a continuously variable transmission that is simple in structure, can be made inexpensive, can be miniaturized, and can change speed without changing the interval between an input shaft and an output shaft.

Claims of the present invention for solving the above 1, the rotation shaft in the center of the outer ring is disposed, the connecting ring is fixed to the rotary shaft, via a plurality of elastic members to the outer ring to the connecting ring The outer ring is sandwiched between a plurality of guide rollers, and the plurality of guide rollers are integrally moved, or an adjustment plate that is moved by driving means is provided on the outer ring. It is characterized by.

A second aspect of the present invention for solving the above-mentioned problems is that, in the first aspect, the connection ring is composed of a plurality of members, and the outer ring is supported by the connection rings via a plurality of elastic members, respectively. Connection means for selectively connecting the rotation shaft and each of the connection rings is provided .

According to the first aspect, the outer ring shifts with forced eccentricity by the movement of the guide roller or the adjustment plate . Since this configuration includes an outer ring, a rotating shaft, a connecting ring, and a plurality of elastic members, the structure is simple and inexpensive, and the size can be reduced. The rotation shaft can be used as an input shaft, and the rotation of the outer ring can be shifted and transmitted to the output shaft without changing the distance between the input shaft and the output shaft.
According to claim 2, in addition to the effect of claim 1, the following effect can be obtained. By selectively engaging the rotating shaft and the plurality of connecting rings by the connecting means, the eccentricity can be made variable by the elastic constant of the elastic member .

According to claims 1 and 2 , the following effects can be obtained in addition to the effects described above . By moving a plurality of guide rows La or the adjustment plate, the outer ring is shifting forcibly eccentric.

A first reference embodiment of the continuously variable transmission according to the present invention will be described with reference to FIGS. As shown in FIG. 1, the continuously variable transmission 1 has the following configuration. A rotating shaft 3 is disposed at the center of the outer ring 2. Four spring hooks 4 are provided on the outer ring 2, and a connection ring 6 having four spring hooks 5 corresponding to the spring hooks 4 is fixed to the rotating shaft 3. A spring 7 is hung on the spring hooks 4 and 5. Since the outer ring 2 is only supported by the rotating shaft 3 via the spring 7, the outer ring 2 may be displaced in the axial direction of the rotating shaft 3. Therefore, guide plates 8 are disposed on both sides of the outer ring 2 with a slight gap from the outer ring 2, and the guide plates 8 are fixed to the rotating shaft 3. Further, in order to restrict the outer ring 2 from moving in the direction perpendicular to the rotating shaft 3, a stopper 9 is fixed to the guide plate 8 at a constant interval from the inner periphery of the outer ring 2. Although not shown in the drawing, the outer ring 2 and the connecting ring 6 are provided with links, cylinders, cables, and the like that restrict the extension of the spring 4 so that the spring 4 does not exceed the elastic limit.

  FIG. 1 shows a state where no load is applied to the outer ring 2. As shown in FIG. 2 from the state of FIG. 1, it is assumed that the rotating shaft 3 is rotated in the direction of arrow A and a load W is applied to the outer ring 2 in the direction of arrow. Since the outer ring 2 is only supported by the rotating shaft 3 by the spring 7, the unloaded outer ring 2 indicated by a two-dot chain line is applied in the load direction (downward) as indicated by the solid line when a load W is applied. Moving. That is, the center O1 of the outer ring 2 moves to the center O2, and is decentered by e with respect to the center O1 of the rotating shaft 3. In this case, the portion 2a of the outer ring 2 has a small radius with respect to the rotating shaft 3, and therefore the speed is reduced. As described above, the outer ring 2 is shifted by the autonomous eccentricity e by the rotational force of the rotating shaft 3 and the load W.

  FIG. 3 shows an example of the application. A pulley 11 is fixed to the output shaft 10, and a belt 12 is hung on the outer ring 2 and the pulley 11. Therefore, as described above, when the rotating shaft 3 rotates in the direction of the arrow A and the outer ring 2 is decentered e as shown by the solid line from the two-dot chain line state, the radius of the 2a portion becomes small. Driven by being decelerated from the speed, the pulley 11 is rotated. Needless to say, the outer ring 2 and the pulley 11 may each be a sprocket and the belt 12 may be a chain.

FIG. 4 shows a second reference embodiment of the continuously variable transmission according to the present invention. The reference form shows a case where a set of four springs 7 arranged radially is attached to one outer ring 2 and one connection ring 6. In the present embodiment, there are three connection rings 6A, 6B, 6C, and these connection rings 6A, 6B, 6C are not fixed to the rotating shaft 3 but are rotatably supported. The outer ring 2 and the connection ring 6A are connected by a plurality of sets of springs 7A as in the above embodiment, and the outer ring 2 and the connection rings 6B, 6C are also a plurality of sets of springs 7B, 7C, respectively. It is connected with.

  The outer ring 2 and the connecting rings 6A, 6B, 6C can be selectively coupled to each other. A key groove 3a is formed in the connecting ring 6A, 6B, 6C of the rotating shaft 3 in the axial direction, and a key 15 is mounted in the key groove 3a so as to be movable in the axial direction. Key grooves 6a and 6b having the same depth are formed in the connection rings 6A and 6B, and a key groove 6c deeper than the key grooves 6a and 6b is formed in the connection ring 6C. The key 15 is formed with a key portion 15a having a low height that engages with the key grooves 6a and 6b and a key portion 15c having a high height that engages with the key groove 6c.

  Therefore, when the key 15 is moved as shown in FIG. 4B (b1), the key portion 15a of the key 15 engages only with the key groove 6b of the connecting ring 6B, and the rotating shaft 3 is connected to the connecting ring 6B. The outer ring 2 is connected to the urging force of the spring 7B. When the key 15 is moved as shown in FIG. 4B (b2), the connecting rings 6A and 6B are connected to the rotary shaft 3, and the urging forces of the springs 7A and 7B act on the outer ring 2. When the key 15 is moved as shown in FIG. 4B (b3), the connecting ring 6C is also engaged with the key portion 15c of the key 15, so that the connecting ring 6A, 6B, 6C is connected to the rotary shaft 3. The outer ring 2 is connected to the urging force of the springs 7A, 7B, 7C.

  In this way, the outer ring 2 is made of the spring 7A by arranging the plurality of radially arranged springs 7A, 7B, 7C in the direction of the plurality of rows and selectively engaging with the rotary shaft 3. , 7B, 7C, the eccentricity can be made variable by the elastic constant. In addition, although the said embodiment demonstrated the case where the three connection rings 6A, 6B, and 6C and three sets of springs 7A, 7B, and 7C were provided, the number of these is not specifically limited, 2 One or more connecting rings and springs may be provided.

Each said reference form shows the structure which the outer ring | wheel 2 carries out a gear shift by autonomous eccentricity with the rotational force of the rotating shaft 3, and the load to the outer ring | wheel 2. FIG. 5 to 10 show a configuration having a shift by forced eccentricity. FIG. 5 shows a case using the guide roller 20 and FIG. 6 shows a case using the adjusting plate 30 for forcibly decentering the outer ring 2.

Figure 5 shows a first embodiment of the continuously variable transmission of the present invention. On the side surface of the outer ring 2, a flange portion 2 c having an outer diameter larger than the outer diameter of the outer ring 2 and an inner diameter substantially the same as that of the outer ring 2 is integrally formed. Four guide rollers 20 are disposed on the outer periphery of the flange portion 2c so as to sandwich the flange portion 2c. The guide roller 20 is rotatably provided on a support shaft 21, and the support shaft 21 is fixed to a moving plate 22. The moving plate 22 is moved by a driving means (not shown) in a direction perpendicular to the paper surface in FIG. 5B, and the moving plate 22 is provided with a hole so as not to interfere with the rotating shaft 3.

  Therefore, when the moving plate 22 is moved in the direction perpendicular to the paper surface in FIG. 5B, the guide roller 20 moves in the direction of the arrow as shown in FIG. Accordingly, the outer ring 2 is moved right or left by the guide roller 20, and the outer ring 2 is eccentric. Therefore, the outer ring 2 is forcibly eccentric and shifts.

Figure 6 shows a second embodiment of the continuously variable transmission of the present invention. In the embodiment, the guide roller 20 is disposed outside the outer ring 2. In this embodiment, the guide roller 20 is disposed inside the outer ring 2. The inner periphery of the flange portion 2c formed integrally with the outer ring 2 is formed smaller than the inner periphery of the outer ring 2, and four guide rollers 20 are formed on the inner periphery of the flange portion 2c so as to sandwich the flange portion 2c. Is arranged. The guide roller 20 is rotatably provided on the support shaft 21 as in the above embodiment, and the support shaft 21 is fixed to the moving plate 22. Thus, even if configured, the same effect as in the above embodiment can be obtained.

FIG. 7 shows a third embodiment of a continuously variable transmission according to the present invention. Four-sided adjustment plates 30 and 30 that are moved by driving means (not shown) are fixed to the side surface of the outer ring 2. The adjustment plate 30 is formed larger than the outer periphery of the outer ring 2, and has a hole 30 a that is the same as or slightly larger than the inner diameter of the outer ring 2. Even if comprised in this way, the effect similar to 1st and 2nd embodiment of FIG.5 and FIG.6 is acquired. That is, when the adjustment plate 30 is moved in the direction of the arrow, the outer ring 2 is also moved in the same direction and is eccentric. As a result, the outer ring 2 shifts with forced eccentricity.

FIG. 8 shows a continuously variable transmission according to a fourth embodiment of the present invention. The present embodiment includes two continuously variable transmissions 1A and 1B, one continuously variable transmission 1A serving as an input unit, and the other continuously variable transmission 1B serving as an output unit. Yes. That is, 3A is an input shaft, 3B is an output shaft, and the input shaft 3A and the output shaft 3B are provided so that the two outer rings 2 and 2 are in contact with each other. Therefore, in the present embodiment, the output shaft 3B is shifted by the forced eccentricity of the outer rings 2 and 2 without using the pulley 11 (or sprocket), the belt 12 (or chain) or the like shown in FIG.

FIGS. 9A and 9B show fifth and sixth embodiments of the continuously variable transmission according to the present invention. In the present embodiment, the first and second embodiments shown in FIGS. 5 and 6 are applied to the embodiment shown in FIG. That is, FIGS. 9A and 9B are similar to FIGS. 5 and 6 in that the outer periphery or the inner periphery of the flange portion 2c (see FIG. 5B) fixed to the side surface of the outer ring 2 is clamped. A number of guide rollers 20 are provided. The guide roller 20 is rotatably provided on a support shaft 21, and the support shaft 21 is fixed to a moving plate 22. Accordingly, in the present embodiment, as in the fourth embodiment of FIG. 8, when the guide roller 20 is moved in the direction of the arrow, the outer ring 2 is moved left or right by the guide roller 20, and the outer ring 2 is eccentric. As a result, the outer ring 2 is forcibly eccentrically shifted.

FIG. 10 shows a seventh embodiment of a continuously variable transmission according to the present invention. This embodiment shows a case where the third embodiment of FIG. 7 is applied to the embodiment of FIG. That is, in FIG. 10, like FIG. 7, four-sided adjustment plates 30, 30 that are moved by a driving means (not shown) are fixed to the side surface of the outer ring 2. The adjustment plate 30 is formed larger than the outer periphery of the outer ring 2, and has holes 30 a and 30 a that are the same as or slightly larger than the inner diameter of the outer ring 2. Therefore, in the present embodiment, when the adjustment plate 30 is moved in the direction of the arrow, the outer ring 2 is also moved in the same direction and is eccentric. As a result, the outer ring 2 shifts with forced eccentricity.

FIG. 11 shows an eighth embodiment of a continuously variable transmission according to the present invention. In each of the above embodiments, the case where the four springs 7 are provided radially on the connecting ring 6 has been described. The number of springs 7 is not limited to four. For example, five springs are provided as shown in FIG. 11 (a), six are provided as shown in FIG. 11 (b), and eight are provided as shown in FIGS. 11 (c) and 11 (d). May be. The attachment method of the spring 7 may be different as shown in FIGS.

  In addition, although each said embodiment demonstrated the case where the spring 7 was provided as an elastic member, it is not limited to the spring 7. FIG. For example, rubber may be used. Needless to say, the structure of FIG. 4 can also be applied to the structures of FIGS.

The 1st reference form of the continuously variable transmission of this invention is shown, (a) is the front view of the state which removed the guide plate, (b) is a side view. It is a front view in the state where the rotating shaft rotated and the load was added to the outer ring. It is a front view showing an example of application. The 2nd reference form of the continuously variable transmission of this invention is shown, (a) is a side view, (b) is explanatory drawing of the engagement relation of a key and a connection ring. 1 shows a first embodiment of a continuously variable transmission according to the present invention, in which (a) is a front view in which guide rollers are arranged on the outer side of an outer ring, and (b) is a side view. The 2nd Embodiment of the continuously variable transmission of this invention is shown, (a) is the front view which arrange | positioned the guide roller in the inner side part of the outer ring | wheel, (b) is a side view. The 3rd Embodiment of the continuously variable transmission of this invention is shown, (a) is a front view, (b) is a side view. It is a front view of 4th Embodiment of the continuously variable transmission of this invention. 5 and 6 show fifth and sixth embodiments of the continuously variable transmission according to the present invention, in which (a) is a front view in which guide rollers are arranged on the outer side of the outer ring, and (b) is a guide roller on the inner side of the outer ring. It is the arranged front view. It is a front view of 7th Embodiment of the continuously variable transmission of this invention. It is a front view of 8th Embodiment of the continuously variable transmission of this invention.

Explanation of symbols

1, 1A, 1B continuously variable transmission 2 outer ring 2c collar 3 rotating shaft 3a key groove 6, 6A, 6B, 6C connecting ring 6a, 6b key groove 7, 7A, 7B, 7C spring 8 guide plate 15 key 20 guide roller 21 Support shaft 30 Adjustment plate

Claims (2)

  A rotating shaft is disposed at the center of the outer ring, a connecting ring is fixed to the rotating shaft, the outer ring is supported by the connecting ring via a plurality of elastic members, and the outer ring is sandwiched by a plurality of guide rollers. A continuously variable transmission characterized in that the plurality of guide rollers are integrally moved, or an adjustment plate that is moved by a driving means is provided on the outer ring. The connecting ring includes a plurality of connecting rings, and the outer ring is supported by the connecting rings via a plurality of elastic members, and connecting means for selectively connecting the rotating shaft and the connecting rings is provided. The continuously variable transmission according to claim 1 .

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