JPWO2019130512A1 - Drive assist device and generator to which it is applied - Google Patents

Abstract

Provided is a small-sized drive assist device having a simple structure, a small number of components, and capable of sufficiently assisting a drive force at low cost. The drive assist device for a bicycle uses the pedal 7a to move the roller 12a of the variable mechanism 9a fitted in the distorted annular guide groove 11a of the guide member 10a to move along the wall. Utilize it. The variable mechanism 9a itself expands and contracts with the movement of the roller 12a, and the distance between the axis of the support shaft 8 and the axis of the pedal 7a in the land portion L is increased on the blunt end side of the groove 11a (the upper part is rounder than the lower part). Small) is longer and shorter at the shrunken sharp end. As a result, the movement of the roller 12a can be made faster at the blunt end side of the groove 11a, and can be made slower at the lower part than at the upper part, and can be made slower with no load at the sharp end side, thereby reducing the load on the foot pedaling the pedal 7a and driving assistance. it can. The pedal 7b for the annular guide groove 11b of the hidden guide member 10b on the opposite side and the roller 12b of the variable mechanism 9b also function similarly.

Description

  The present invention relates to a drive assist device that can effectively assist driving of a bicycle or the like and a generator to which the drive assist device is applied.

  2. Description of the Related Art Conventionally, in general bicycles, a transmission that varies a load on a foot when a user pedals is often mounted in order to make a comfortable run. However, such a transmission cannot change the running speed by switching the transmission gear, but cannot reduce the total amount of motion of the foot when pedaling.

  Therefore, as a well-known technology that has solved such inconvenience, there is a “drive booster” (see Patent Document 1) that effectively reduces the burden on a foot that always pedals during traveling.

Japanese Patent No. 5571420

  The above-described drive booster according to Patent Literature 1 is designed to increase the drive force of the bicycle and to act on the rear wheels. In one embodiment, each of these is provided by a movable rotation pin rotatably inserted through the first swing link and a rotatable support shaft rotatably attached to the other end of the second swing link and fixed to one end thereof. A first plate-like rod is fixed between the link and a moving rotation axis that cooperates with the movement of the link. The first swing link here is swingable by a first rotating shaft rotatably inserted. The first plate-shaped rod reciprocates by moving the rotating pin and the rotating shaft alternately. Further, when the rolling shaft fixed to one end of the second plate-like rod fixed to the moving fixed shaft is fitted into the groove of the crank and moves in the groove, the crankshaft is moved from a position at a short distance from the moving rotary shaft. It is moved to a position at a long distance from the rotatable second rotation shaft fixed to the other end. At this time, since the rotation can be performed while the lever action is generated temporarily, the driving force is increased at the portion where the lever action occurs.

  In this drive booster, the movement within half a rotation when the actual pedal is pedaled, the longer the movement distance from the support shaft to the second rotation shaft, the shorter the movement distance from the rotation center to the second rotation shaft. It becomes movement and can move fast. In addition, the movement within half a rotation when pedaling the actual pedal becomes a movement in which the movement distance from the rotation center to the second rotation axis becomes longer if the movement distance from the support shaft to the second rotation axis is shortened, and the movement is slow. be able to.

  However, according to this technique, there is a problem that the structure of the swing link mechanism is complicated, the number of parts is large, and high cost cannot be avoided. In addition, since the swing link mechanism is attached to the rear portion of the saddle (saddle) of the seating portion, the dimensions of the entire base (frame) from the front wheel to the rear wheel become longer, so that the size cannot be avoided. Another problem is that it cannot meet the demand for miniaturization.

  SUMMARY OF THE INVENTION The present invention has been made to solve such a problem, and its technical problem is to provide a small-sized drive that is simple in structure, has a small number of parts, and is capable of providing sufficient driving force at low cost. An object of the present invention is to provide an auxiliary device and a generator to which the auxiliary device is applied.

  In order to solve the above technical problems, one embodiment of the present invention provides a support shaft rotatably supported on a base, a pedal that applies a rotational force to the support shaft, and a support shaft and a pedal attached to the support shaft. When movable, a variable mechanism capable of changing the distance between the support shaft and the pedal, and a guide member fixed to the base so as to face the variable mechanism by inserting the support shaft at an eccentric position, A transmission mechanism for transmitting the rotation of the support shaft to the transmitted portion, wherein the guide member is provided with an annular guide groove that extends in a non-circular and annular shape around the support shaft, and is variable. The mechanism has an engaging body movable along a wall of the annular guide groove.

  According to the present invention, with the above configuration, it is possible to provide a small-sized drive assist device that has a simple structure, has a small number of parts, and can sufficiently assist the drive force at low cost. Problems, configurations, and effects other than those described above will be apparent from the following description of the embodiments.

1 is a perspective view illustrating a schematic configuration of a bicycle to which a drive assist device according to a first embodiment of the present invention is applied. FIG. 2 is a perspective view schematically showing a structure of a variable mechanism and a guide member, which are main parts of the drive assist device shown in FIG. 1. FIGS. 3A and 3B are diagrams illustrating respective members in a case where the guide member illustrated in FIG. 2 is configured to be assembled with another member, wherein FIG. 3A illustrates a reinforcing substrate, FIG. 3B illustrates an outer guide member, and FIG. FIG. 4 is a view showing a land portion. 4A and 4B are diagrams illustrating an assembly structure of a guide member in which the members illustrated in FIG. 3 are assembled, wherein FIG. 4A is a plan view and FIG. 4B is a side sectional view. FIGS. 2A and 2B illustrate a structure for reinforcing a guide member illustrated in FIG. 2, wherein FIG. 2A is a plan view of a guide member including a reinforcing member, and FIG. 2B is a cross-sectional view in the vertical direction near the center of gravity of FIG. is there. FIG. 3 is a schematic diagram illustrating a state in which a roller of the variable mechanism described in FIG. 2 is fitted into an annular guide groove of a guide member and moves. FIG. 2 is a partially cutaway perspective view showing a detailed structure of a variable mechanism and a transmission mechanism, which are main parts of the drive assist device shown in FIG. 1. FIG. 7 is a perspective view illustrating a schematic configuration of a generator to which the drive assist device according to the second embodiment of the present invention is applied.

  Hereinafter, a drive assist device of the present invention and a generator to which the drive assist device is applied will be described in detail with reference to the drawings, using several embodiments.

  FIG. 1 is a perspective view illustrating a schematic configuration of a bicycle to which the drive assist device according to the first embodiment of the present invention is applied.

  Referring to FIG. 1, the bicycle integrally includes a head tube 1a, a top tube 1b, a down tube 1c, a seat tube 1d, a seat stay 1e, and a chain stay 1f as a frame serving as a base. A handlebar 2 is mounted on the upper side of the head tube 1a via a stem, and a front suspension 4 is mounted on a lower side. A handle 2 ′ is attached to the distal end of the handle bar 2. The front wheel 5 attached to the front suspension 4 has a structure in which a tire 5b is attached outside a rim 5a provided with a plurality of spokes inside. A saddle 3 is attached to a connection portion between the top tube 1b and the seat stay 1e of the seat tube 1d via a seat pillar. The rear wheel 6 attached to the distal ends of the seat stay 1e and the chain stay 1f also has a structure in which a tire 6b is attached to the outside of a rim 6a provided with a plurality of spokes inside. The spokes of both the front wheel 5 and the rear wheel 6 are illustrated in a simplified manner.

  Further, an insertion shaft 18 is rotatably inserted into the chain stay 1f, and a second gear 14 and a third gear 15 opposed thereto are mounted and fixed to the insertion shaft 18. The third gear 15 is usually called a chain wheel, and the second chain C2 is bridged along with the fourth gear 16 attached to and fixed to the support shaft 23 of the rear wheel 6. A transmission for shifting the rotational movement of the second chain C2 is attached to the fourth gear 16 as necessary. The parts described above have the same configuration as a general bicycle.

  The drive assist device according to the first embodiment includes a support shaft 8 that is rotatably supported on the frame through the frame, and a pair of pedals 7a and 7b that apply a rotational force to the support shaft 8. The pedal 7b is hidden in FIG. Further, the drive assist device has a pair of variable mechanisms 9a, which can change the distance between the support shaft 8 and the pedals 7a, 7b when the support shaft 8 and the pedals 7a, 7b are attached and move. 9b. The variable mechanism 9b is hidden in FIG. Further, the drive assist device transmits the rotation of the support shaft 8 to the pair of guide members 10a and 10b fixed to the frame so that the support shaft 8 is inserted at the eccentric position and faces the variable mechanisms 9a and 9b. And a transmission mechanism for transmitting to the rear wheel 6 serving as a part.

  More specifically, the guide members 10a and 10b are provided with a distorted circular land portion L at the center portion, and the support shaft 8 is located at an eccentric position corresponding to the land portion L on the rear side of the frame. It is inserted including the frame. In addition, annular guide grooves 11a and 11b are provided extending non-circularly and annularly along the periphery of the land portion L. The annular guide groove 11b and the land portion L of the guide member 10b are hidden in FIG. The guide members 10a and 10b having such a structure can be integrally manufactured by using, for example, a mold. However, in the case of such a structure, the roller 12a does not deform in a predetermined region between the lower neighboring wall of the annular guide grooves 11a and 11b and the upper neighboring wall of the land L even if the roller 12a moves by applying pressure. As described above, it is preferable to connect a hard reinforcing member as necessary, or to strengthen the hardness by quenching or the like. Further, the shaft hole for inserting the support shaft 8 in the land portion L can be made considerably larger than the diameter of the support shaft 8.

  The variable mechanisms 9a and 9b have rollers 12a and 12b that are fitted into the annular guide grooves 11a and 11b and that can move on their walls. The roller 12b of the variable mechanism 9b is hidden in FIG. The rollers 12a, 12b themselves have a structure in which a ball-shaped or round-bar-shaped bearing built in to rotate a contact portion (shaft) of the annular guide grooves 11a, 11b with a wall is attached to a pin. 10b move along the walls of the annular guide grooves 11a and 11b. Thereby, the variable mechanisms 9a, 9b cooperate with the guide members 10a, 10b, and the rollers 12a, 12b move along the walls of the annular guide grooves 11a, 11b while expanding and contracting themselves as described later. Functions as a crank mechanism. Incidentally, the rollers 12a and 12b can be configured so as to slide on the concave surfaces of the annular guide grooves 11a and 11b, and can also be configured not to slide. If the rollers 12a and 12b do not slide on the concave surfaces of the annular guide grooves 11a and 11b, the burden on the feet for pedaling the pedals 7a and 7b can be reduced. For the rollers 12a and 12b, for example, a THK ball spline miniature ball spline LSB type or ball spline LSB type, or a THK LM system linear motion system / rotary motion type cam follower can be used.

  By the way, the land L is not necessarily required in terms of the operation principle. If a distorted circular guide concave portion which is depressed and developed non-circularly around the support shaft 8 without the land L is provided, the roller 12a , 12b move along the wall of the guide recess. Further, in this case, the support shaft 8 is configured to be directly inserted into the concave surface of the guide concave portion at the eccentric position corresponding to the rear side of the frame. Also in this case, the shaft hole for inserting the support shaft 8 can be made considerably larger than the diameter of the support shaft 8. In the structure of the guide members 10a and 10b, in the guide recess, a land portion L through which a distorted circular support shaft 8 is inserted at an eccentric position corresponding to the rear side of the frame is provided as a separate member. For example, annular guide grooves 11a and 11b are formed between the wall of the guide recess and the wall of the land L. Therefore, even in such an assembled structure, it can be considered that the structure is the same as the case where it is integrally formed.

  FIG. 2 is a perspective view schematically showing the structures of the variable mechanism 9a and the guide member 10a, which are main parts of the above-described drive assist device.

  Referring to FIG. 2, when the pedal 7a is pedaled, the roller 12a of the variable mechanism 9a moves along the wall while being fitted into the annular guide groove 11a of the guide member 10a. The annular guide groove 11a of the guide member 10a has a distorted annular shape in which a portion corresponding to the front side in the frame is a blunt end and a portion corresponding to the rear side is an acute end. Further, the annular guide groove 11a has a large roundness (so-called R) on the blunt end side, and the upper roundness on the blunt end side is smaller than the lower roundness. Similarly, for the contour shape of the distorted circular land portion L and the guide member 10a, a portion corresponding to the front side is a blunt end, and a portion corresponding to the rear side is a sharp end. Incidentally, even in the case of the guide concave portion having no land portion L, a similar distorted circular shape is obtained. As described above, the support shaft 8 is rotatably inserted into the eccentric position of the guide member 10a including the frame at a position closer to the acute end side of the land L inside the annular guide groove 11a. The contour shape of the guide member 10a may be changed to a shape other than the illustrated one, for example, a substantially square shape. The guide members 10a and 10b have annular guide grooves 11a and 11b, and various configurations can be applied as exemplified below, and the overall weight can be reduced.

  FIGS. 3A and 3B are diagrams illustrating each member in a case where the guide member 10a is formed as an assembling structure by another member. FIG. 3A illustrates the reinforcing substrate LB, and FIG. 3B illustrates the outer guide member GO. FIG. 3C is a diagram showing a land portion L. FIG. 4A and 4B are views showing an assembling structure of the guide member 10a in which the respective members are assembled, wherein FIG. 4A is a plan view and FIG. 4B is a cross-sectional view from the side.

  As an example of an assembling structure of the guide member 10a, as shown in FIGS. 3A to 3C, a shaft hole serving as an inner guide member for a reinforced substrate LB having the same circular shape as the contour shape of the guide member 10a. There is a case where the land portion L provided with the LH and the outer guide member GO having a distorted annular shape are assembled. The shaft hole LH is provided at an eccentric position of the land L near the acute end. In this case, a screw hole for positioning and fixing is drilled in advance at a predetermined position of the reinforcing substrate LB, and the land portion L is screwed to the reinforcing substrate LB with a tap T interposed so as to maintain a predetermined height. And attach it. Thereafter, an outer guide member GO is screwed to the reinforcing substrate LB around the land portion L with a similar tap T interposed therebetween, and an annular member is formed between the inner side of the outer guide member GO and the outer side of the land portion L. What is necessary is just to assemble so that the guide groove 11a may be formed. The assembly procedure described here may be reversed. As a result, an assembly structure as shown in FIGS. 4A and 4B is obtained. Instead of the land portion L, a grooved land portion having a concave annular guide groove 11a formed around the convex land portion L may be used as the inner guide member. The grooved land portion is larger than the land portion L alone because the annular guide groove 11a is integrally formed around the land portion L.

  FIG. 5 illustrates a structure for reinforcing the guide member 10a shown in FIG. 2, wherein FIG. 5 (a) is a plan view of the guide member 10a provided with the reinforcing members D1 and D2, and FIG. FIG. 3 is a vertical sectional view near the center of gravity of FIG.

  5 (a) and 5 (b), a hard reinforcing member D1 is coupled to a predetermined region of the lower neighboring wall portion in the annular guide groove 11a of the guide member 10a, and the upper neighboring wall of the land portion L is formed. A hard reinforcing member D2 is also coupled to a predetermined region in the portion, and measures are taken to prevent deformation even when the roller 12a moves by applying pressure. Instead of the reinforcing members D1 and D2, it is also possible to strengthen the hardness by quenching or the like in a similar region. Here, the guide member 10a having the integrated structure shown in FIG. 2 has been described as an example, but such a reinforcing measure is the guide member having the assembly structure described with reference to FIGS. 3, 4A, and 4B. The same applies to 10a. Incidentally, in any of these structures, the shaft hole LH for inserting the support shaft 8 can be considerably larger than the diameter of the support shaft 8.

  As another example of the assembling structure of the guide member 10a, there is a case of using a distorted annular plate member that has been processed in advance on a distorted reinforcing substrate LB having the same distorted circular shape as the contour shape of the guide member 10a. In this case, a screw hole for positioning and fixing is drilled in advance at a predetermined position of the reinforcing substrate LB, and a tap T is formed so that the small annular outer plate member serving as an inner guide member has a predetermined height. It is screwed and attached to the reinforcing substrate LB with intervening. Thereafter, a large-diameter strain annular plate member serving as the outer guide member GO is attached to the reinforcing substrate LB with screws around the small-diameter distortion annular plate member around the same tap T. Assembling such that the annular guide groove 11a is formed between the inside of the large distorted annular plate member (outer guide member GO) and the outside of the small external distorted annular plate member (inner guide member). good. The assembly procedure described here may be reversed.

  In such an assembling structure as well, a predetermined area between the lower vicinity wall of the outer guide member GO and the upper vicinity wall of the inner guide member is hard so that the roller 12a is not deformed even if it is moved by applying pressure. It is preferable to combine the reinforcing members D1 and D2 or to strengthen the hardness by quenching or the like. Also, in this structure, only the outer distorted annular plate member serving as the outer guide member GO may be provided on the reinforcing substrate LB on the basic function, and the inner distorted annular plate member on the inner wall side may be provided. Thus, a guide concave portion which is depressed and developed in a non-circular shape is formed. In any structure, the shaft hole LH for inserting the support shaft 8 provided in the reinforcing substrate LB can be considerably larger than the diameter of the support shaft 8.

  As another example of the assembling structure of the guide member 10a, the frame is deformed without using the reinforcing substrate LB to add a reinforcing portion, and the inner guide member and the outer guide member GO are directly connected to the frame. There are cases. In this case, when the member described in the example of the assembling structure is used, a distorted circular land portion L serving as an inner guide member with respect to the frame, and a large outer distorted annular plate member serving as an outer guide member GO therearound. And the annular guide groove 11a may be formed between the inside of the outer guide member GO and the outside of the land portion L. When the member described in the other example of the assembling structure is used, the distorted ring-shaped plate member having a small inner outer shape serving as the inner guide member and the large-distortion ring-shaped plate member having the outer outer shape serving as the outer guide member GO are connected. The annular guide groove 11a may be formed between the inside of the distorted annular plate member having a large external shape and the outside of the distorted annular plate member having a small external shape.

  In the former case in another example of the assembling structure, the support shaft 8 has a structure in which the eccentric position near the sharp end side of the land portion L and the frame are inserted, and supports the shaft hole LH through which the support shaft 8 is inserted. It can be considerably larger than the diameter of the shaft 8. In the latter case, the structure is such that the support shaft 8 only penetrates the frame directly. In such a structure, since the concave surface of the reinforcing substrate LB does not exist in any case, the roller 12a of the variable mechanism 9a is fitted into the annular guide groove 11a of the guide member 10a when the pedal 7a is pedaled. The movement moves along the part. Incidentally, even in an example of the assembling structure, by selecting the height of the tap T and the screwing dimension, an assembling structure in which the roller 12a does not slide without contacting the concave surface of the reinforcing substrate LB can be obtained. Similarly, in the integrated guide member 10a, if the annular guide groove 11a is made deeper to some extent, the roller 12a of the variable mechanism 9a can be configured to not slide without contacting the concave surface.

  In any case, the guide member 10a may be formed with a guide recess or an annular guide groove 11a, and although there is a difference in a detailed configuration depending on an assembling structure or a manufacturing method, any shape may be used. And The annular guide groove 11a of the guide member 10a according to the first embodiment is formed so that the roller 12a of the variable mechanism 9a can move along the wall without contacting the concave surface. The guide member 10b also has a similar structure in which a portion corresponding to the front side of the frame is a blunt end of the annular guide groove 11b.

  In the variable mechanism 9a, a support shaft 8 is fixedly mounted on a plate-like piece 9a-1 on one end side facing the guide member 10a. Further, a part of the slide groove V of the plate-shaped piece 9a-1 is engaged, and the movable piece 9a-2 on the other end side facing the guide member 10a has a shape that sandwiches the plate-shaped piece 9a-1. Along with the plate-like piece 9a-1. Further, a pedal 7a is rotatably mounted around the axis at a position on the other end side of the movable piece 9a-2 on the outer side, and an inner end of the movable piece 9a-2 corresponding to between the support shaft 8 and the pedal 7a. A roller 12a is attached to a location on the side. In addition, an elongate hole 26 is provided at a position from the pedal 7a on the other end side of the movable piece 9a-2 to the one end side, and a pin-shaped projection 27 abuts on a wall portion inside the elongate hole 26. 26 is configured to regulate the displacement.

  The shape of the slide groove V of the plate-like piece 9a-1 and the shape of the engaging portion of the movable piece 9a-2 engaged with the slide groove V can be variously changed. For example, LAH-AN type of LH series of NSK linear guide can be applied. This is a type in which ball bearings are built in a slide groove V, and two V grooves are provided at both corners and two V grooves are provided on left and right side surfaces. Also, this is a centering type LN series linear guide for industrial machines, and an LN series square AN-AL type having two V-grooves on the left and right side surfaces can be applied. Furthermore, THK LM guides for compact heavy load or medium load LM guide SR type (various rail shapes), LM guide VSR-TBA type (some types have no groove), LM guide HSR-TA type (ultra heavy A load type without a ball bearing inside the block) and an LM guide HRV type (four-way equal load type with a long width) can be applied. In addition, an FT type or FTW type needle bearing of the TMK LM system is also applicable.

  In the variable mechanism 9a having such a structure, when the pedals 7a are rowed while the rollers 12a are fitted into the annular guide grooves 11a, the rollers 12a themselves expand and contract as the rollers 12a move along the walls of the annular guide grooves 11a. I do. At this time, the engagement portion of the movable piece 9a-2 moves along the slide groove V of the plate-like piece 9a-1, and the elongated hole 26 is displaced, so that the axis of the support shaft 8 and the axis of the pedal 7a are displaced. The distance is variable. The variable mechanism 9b and the guide member 10b have the same configuration except that the directions are opposite.

  FIG. 6 is a schematic diagram showing a state in which the roller 12a of the variable mechanism 9a described in FIG. 2 is fitted into the annular guide groove 11a of the guide member 10a and moves.

  FIG. 6 shows a state in which the variable mechanism 9a itself expands and contracts when the roller 12a of the variable mechanism 9a is fitted into the annular guide groove 11a of the guide member 10a and moves, assuming a case where the pedal 7a is rowed counterclockwise. ing. The expansion and contraction of the variable mechanism 9a itself indicates a change in the distance (crank length) between the axis of the support shaft 8 and the axis of the pedal 7a.

  More specifically, at position A, the pedal 7a is at the top, and the roller 12a is guided by the distorted annular annular guide groove 11a, so that the distance between the axis of the support shaft 8 and the axis of the pedal 7a is medium. Length. At the position B, the pedal 7a is at a position slightly lower than the top, and the distance between the axis of the support shaft 8 and the axis of the pedal 7a is considerably long. At the position C, the pedal 7a is at a middle height position, and the distance between the axis of the support shaft 8 and the axis of the pedal 7a is the longest. Note that the crank length becomes maximum at a position slightly closer to the position C between the position B and the position C. At the position D, the pedal 7a is located slightly higher than the lowest point, and the distance between the axis of the support shaft 8 and the axis of the pedal 7a is slightly longer. Incidentally, the distance between the axis of the support shaft 8 and the axis of the pedal 7a at the position D is shorter than the distance between the axis of the support shaft 8 and the axis of the pedal 7a at the position B.

  At the position E, the pedal 7a is at the lowest point, and the distance between the axis of the support shaft 8 and the axis of the pedal 7a is slightly shorter. Incidentally, the distance between the axis of the support shaft 8 at the position E and the axis of the pedal 7a may be referred to as a reference crank length, and the distance between the axis of the support shaft 8 at the position A and the axis of the pedal 7a may be referred to as the reference crank length. Shorter than the distance. At the position F, the pedal 7a is located at a position slightly higher than the position D, and the distance between the axis of the support shaft 8 and the axis of the pedal 7a is considerably shorter. At the position G, the pedal 7a is at an intermediate height position, and the distance between the axis of the support shaft 8 and the axis of the pedal 7a is the shortest. At the position H, the pedal 7a is located at a position slightly lower than the position B, and the distance between the axis of the support shaft 8 and the axis of the pedal 7a is considerably shorter. Incidentally, the distance between the axis of the support shaft 8 and the axis of the pedal 7a at the position H is shorter than the distance between the axis of the support shaft 8 and the axis of the pedal 7a at the position F.

  That is, in the drive assisting device according to the first embodiment, as shown in FIG. 6, the roller 12a of the variable mechanism 9a fitted in the distorted annular annular guide groove 11a of the guide member 10a by pedaling the pedal 7a has a wall portion. Utilizes the action of the moment of force when moving along. In general, if the axis of the support shaft 8 is located near the center of the guide member 10a (land portion L), a structure in which the distance between the axis of the support shaft 8 and the axis of the pedal 7a changes is adopted. Since the variable mechanism 9a itself has a small amount of expansion and contraction, if the pedal 7a is continuously pedaled with a constant force, the annular guide groove 11a moves slowly on the blunt end side which is expanded in shape, and moves fast on the contracted sharp end side. . Thus, in the drive assist device according to the first embodiment, the variable axis mechanism is inserted by inserting the axis of the support shaft 8 at a position near the sharp end of the land portion L sufficiently separated from the vicinity of the center of the guide member 10a at an eccentric position. 9a itself has a large amount of expansion and contraction. Then, with the movement of the roller 12a in the annular guide groove 11a, the distance between the axis of the support shaft 8 and the axis of the pedal 7a is increased due to the expansion and contraction of the variable mechanism 9a itself. The structure of the crank mechanism is devised so that it becomes longer on the end side and shorter on the contracted sharp end side.

  Hereinafter, the operation of the crank mechanism will be described on the assumption that the rotation speed of the support shaft 8 is set to the same constant speed. In the crank mechanism, since the crank length at the position A → E of a half rotation on the blunt end side of the annular guide groove 11a that is bulged in shape is longer than the reference crank length, the movement of the roller 12a can be easily increased. When the transmission is used, the movement of the roller 12a can be made faster with a lighter gear, and the movement of the roller 12a becomes slower with a heavy gear. Moreover, since the upper roundness on the blunt end side is smaller than the lower roundness, if the movement of the roller 12a at the position B → C in the region where the crank length is long is made faster than the movement of the roller 12a at the position C → D The burden on the foot pedaling the pedal 7a is reduced.

  Furthermore, the crank length at the position E → A of the shape-reduced half-rotation on the acute end side in the annular guide groove 11a is shorter than the reference crank length, and the movement of the roller 12a is slowed down accordingly. Actually, it is not necessary to step on the pedal 7a at the position E → A corresponding to the half rotation, and the movement of the roller 12a can be slowed by merely putting the foot on the pedal 7a. By eliminating the burden on the foot at the position E → A on the sharp end side, the load on the foot pedaling the pedal 7a at the position A → E on the blunt end side can be reduced. As a result, the moment of the force acts by the function of the crank mechanism, and the burden of pedaling the pedal 7a with the foot can be reduced, in the same manner as the function of increasing the driving force in the portion where the lever action occurs as described in Patent Document 1. . The operation of pedaling the pedal 7a with the foot may be performed almost in a concentrated manner at the position A → D, and it is almost unnecessary to pedal the pedal 7a at the position E → H.

  FIG. 7 is a perspective view, partially cut away, showing the detailed structures of the variable mechanisms 9a and 9b and the transmission mechanism, which are the main parts of the above-described drive assist device.

  In FIG. 7, when the pedals 7a and 7b are moved in the variable mechanisms 9a and 9b, the movable pieces 9a-2 and 9b-2 can move along the slide grooves V of the plate-shaped pieces 9a-1 and 9b-1. Further, a state in which the displacement of the elongated hole 26 is regulated by the pin-shaped projection 27 is shown. Thereby, the variable mechanisms 9a and 9b extend and contract respectively when the pedals 7a and 7b are rowed. In addition, in FIG. 4, the transmission mechanism is inserted rotatably through the first gear 13 fixed to the support shaft 8 and the chain stay 1f (see FIG. 1) behind the guide members 10a and 10b. And the second gear 14 attached and fixed to the inserted shaft 18.

  Further, referring to FIG. 1, the transmission mechanism is attached and fixed to the first chain C <b> 1 bridged between the first gear 13 and the second gear 14 and the insertion shaft 18 so as to face the second gear 14. And a third gear 15 that is provided. Further, the transmission mechanism has a fourth gear 16 attached and fixed to the support shaft 23 of the rear wheel 6, and a second chain C2 bridged between the third gear 15 and the fourth gear 16. In addition, the transmission mechanism has a transmission schematically illustrated that is attached to the support shaft 23 and that changes the rotational movement of the second chain C2.

  Next, the operation of the transmission mechanism of the bicycle according to the first embodiment will be described. In this transmission mechanism, when the pedals 7a and 7b are pedaled, the rollers 12a and 12b of the variable mechanisms 9a and 9b fitted in the annular guide grooves 11a and 11b of the guide members 10a and 10b respectively correspond to the wall portions of the annular guide grooves 11a and 11b. Move along. Accordingly, the variable mechanisms 9a and 9b rotate while expanding and contracting themselves, and the first gear 13 rotates according to the rotation of the support shaft 8 receiving the rotation. Since the first chain C1 is bridged between the first gear 13 and the second gear 14, the second gear 14 rotates together with the insertion shaft 18 as the first chain C1 rotates. I do. When the second gear 14 rotates, the third gear 15 also rotates together with the insertion shaft 18. Since the second chain C2 is bridged between the third gear 15 and the fourth gear 16 fixedly attached to the support shaft 23, the fourth chain 16 is moved in accordance with the rotational movement of the second chain C2. The gear 16 also rotates with the support shaft 23. As a result, the rotation of the support shaft 8 accompanying the rotation of the variable mechanisms 9a, 9b when the pedals 7a, 7b are rowed is transmitted to the rear wheels 6, and the bicycle can run.

  Incidentally, when the transmission is mounted on the fourth gear 16, the driver sets the gear of the transmission by a switching operation function (not shown) provided on the handlebar 2 'on the distal end side of the handlebar 2. Then, the gear is switched to the gear having the diameter selected by the transmission. With the lightest gear, the load on the feet for pedaling the pedals 7a and 7b can be reduced and the rotation speed can be increased. In the heaviest gear, the load on the foot pedaling the pedals 7a and 7b increases, and the rotation slows down. When the transmission is a gearbox, a large rotation of the input shaft results in a slow rotation, and a small rotation of the output shaft results in a fast rotation. When the transmission is a speed reducer, the reverse is true. When the shaft diameter of the input shaft is small, the rotation is fast, and when the shaft diameter of the output shaft is large, the rotation is slow.

  In any case, in the bicycle to which the drive assist device according to the first embodiment is applied, as described with reference to FIG. 6, when the pedals 7a and 7b are pedaled, the variable mechanisms 9a and 9b and the guide members 10a and 10b cooperate. The moment of force acts due to the function of the working crank mechanism. At this time, while the variable mechanisms 9a and 9b expand and contract themselves, the movement of the rollers 12a and 12b on the blunt end side of the annular guide grooves 11a and 11b of the guide members 10a and 10b that are bulged in shape can be easily and quickly performed with a low load. In addition, the movement can be slower in the lower part than in the upper part on the blunt end side. Further, the movement of the rollers 12a, 12b on the sharpened and sharp ends of the annular guide grooves 11a, 11b can be slowed down without load by eliminating the need to pad with the feet. As a result, the load on the feet for pedaling the pedals 7a and 7b can be reduced and the driving can be sufficiently assisted.

  FIG. 8 is a perspective view illustrating a schematic configuration of a generator to which the drive assist device according to the second embodiment of the present invention is applied.

  Referring to FIG. 8, the generator according to the second embodiment is obtained by modifying the bicycle shown in FIG. 1 to be a non-traveling installation type without providing the front wheel 5 and the rear wheel 6, and having the center axis of the support shaft 23. ′, And a power generation motor 22 as power generation means having a rotating shaft. For this reason, the top tube 1b, the down tube 1c, and the seat tube 1d of the frame serving as the base body have substantially the same shape as in the first embodiment, but the other shapes are changed. The power generation motor 22 can be applied to either a direct current (DC) type or an alternating current (AC) type.

  Specifically, the head tube 1a 'is of a long type that does not require the attachment of the front suspension 4, and the front leg 1g is integrally attached to the lower side. The seat stays 1e 'and the chain stays 1f' are integrally formed with triangular frame portions at locations extending rearward on both sides, and rear legs 1h are integrally mounted on both lower sides. The rear triangular frame portion and the rear leg 1h are hidden in FIG.

  Further, at a position near the seat tube 1d between the pair of triangular frame-shaped portions, a third gear 15 'and a fourth gear 16' are attached to a fourth gear 16 'at one end of a central shaft 23'. A transmission 21 is provided for increasing the rotational movement of the second chain C2 bridged over the gear 16 '. Further, a third chain C3 is bridged between a rear portion between the pair of triangular frame-shaped portions and a fourth gear 16 ″ attached to the other end of the support shaft 23 ′ of the transmission 21. A power generation motor 22 is provided in which the fifth gear 17 is mounted and fixed to the rotating shaft 24. Here, a special mounting tool is separately used to mount the transmission 21 and the power generation motor 22. Alternatively, a dedicated mounting piece may be integrally formed on the frame in advance.

  Incidentally, the third gear 15 of the first embodiment is a chain wheel, but the third gear 15 ′ of the second embodiment uses the same type as the first gear 13 and the second gear 14. In addition, a handlebar 2 is attached to the upper side of the head tube 1a 'via a stem, and a saddle 3 is attached to a connection portion between the top tube 1b and the seat stay 1e' of the seat tube 1d via a seat pillar. Can be

  Further, in the generator according to the second embodiment, the outer shapes of the movable pieces 9a'-2 and 9b'-2 of the variable mechanisms 9a 'and 9b' to which the pedals 7a and 7b are attached are partially lengthened, and The upright portion at one end is modified so as to be connected to the plate-like pieces 9a'-1 and 9b'-1. The plate-like piece 9b'-1 and the movable piece 9b'-2 of the variable mechanism 9b 'and the pedal 7b are hidden in FIG. A rack and pinion 19a for converting the rotational force of the variable mechanism 9a 'into a linear motion is attached to one end of the plate-shaped piece 9a'-1 of the variable mechanism 9a'. The variable mechanism 9b 'has the same configuration except that the direction is reversed. The plate-shaped piece 9b'-1 includes a rack and pinion 19b for converting the rotational force of the variable mechanism 9b' into a linear motion. Installed. The rack and pinion 19b is hidden in FIG.

  These rack and pinions 19a and 19b have a structure in which a circular gear is sandwiched between a pair of bar-shaped racks that are cut off. The upper bar rack moves in the same direction as the variable mechanisms 9a 'and 9b', and the lower bar rack with the weight 25 attached to the tip end moves in the opposite direction to the upper bar rack by the action of the circular gear. For this reason, when the weight 25 moves in the direction in which the upper bar-like rack moves backward, the weight 25 has a hole through which it is inserted. In the rack and pinions 19a and 19b, the weight 25 is moved so that the variable mechanisms 9a 'and 9b' and the weight 25 are balanced about the support shaft 8. The bar-shaped racks in the rack-and-pinion 19a, 19b are fixed so as not to come off by being sandwiched by fixing pieces 20a, 20b. The fixing piece 20b is hidden in FIG.

  Incidentally, the structure of the variable mechanisms 9a ', 9b' provided with the rack-and-pinions 19a, 19b has a function of moving the weight 25 in the opposite direction when the variable mechanisms 9a ', 9b' expand and contract themselves, thereby providing a balance. Therefore, the present invention may be applied to the bicycle of the first embodiment. In addition, in the generator according to the second embodiment, the weight 25 is attached to the tip side of the lower bar-shaped rack of the rack-and-pinions 19a and 19b. However, the weight 25 is not attached if weight reduction is important. It is good. Further, if the rack and pinions 19a, 19b are not required, they need not be provided to the variable mechanisms 9a ', 9b'.

  Next, the operation of the transmission mechanism of the generator according to the second embodiment will be described. In this transmission mechanism, when the pedals 7a and 7b are pedaled, the rollers 12a and 12b of the variable mechanisms 9a 'and 9b' fitted respectively in the annular guide grooves 11a and 11b of the guide members 10a and 10b respectively move the annular guide grooves 11a and 11b. Move along the wall. Accordingly, the variable mechanisms 9a 'and 9b' rotate while expanding and contracting themselves, and the first gear 13 rotates according to the rotation of the support shaft 8 receiving the rotation. Since the first chain C1 is bridged between the first gear 13 and the second gear 14, the second gear 14 rotates together with the insertion shaft 18 as the first chain C1 rotates. I do. When the second gear 14 rotates, the third gear 15 'also rotates together with the insertion shaft 18.

  Since the second chain C2 is bridged between the third gear 15 'and the fourth gear 16' fixed to one end of the support shaft 23 'of the transmission 21, the second chain C2 The fourth gear 16 'also rotates together with the support shaft 23' with the rotational movement of. Accordingly, the fourth gear 16 ″ attached to the other end of the support shaft 23 ′ of the transmission 21 also rotates together with the support shaft 23 ′. The fourth gear 16 ″ and the rotation shaft 24 of the power generation motor 22 Since the third chain C3 is bridged between the third chain C3 and the third chain C3, the rotational movement of the third chain C3 is also changed with the rotational movement of the second chain C2. As a result, the rotation of the support shaft 8 accompanying the rotation of the variable mechanisms 9a ', 9b' when the pedals 7a, 7b are pedaled is transmitted so as to change the speed of the rotation shaft 24 of the power generation motor 22, so that the power can be generated. Become.

  Also in the generator to which the drive assist device according to the second embodiment is applied, as described with reference to FIG. 6, when the pedals 7a and 7b are pedaled, the variable mechanisms 9a 'and 9b' and the guide members 10a and 10b cooperate. The moment of force acts on the function of the working crank mechanism. As a result, the load on the feet for pedaling the pedals 7a and 7b can be reduced, and the drive can be sufficiently assisted on the support shaft 23 'of the transmission 21. As a result, it is possible to control the power generated by shifting the rotation shaft 24 of the power generation motor 22.

  As described above, the transmission 21 includes a speed increaser and a speed reducer, as described above. How to obtain the power generated by shifting the rotation shaft 24 of the power generation motor 22 depends on the type of the power generator. It should just be adopted according to. In general, a reduction gear should be used to suppress power generation, and a speed-up gear should be used to increase power generation. In the case of the drive assist device according to the second embodiment, it is preferable to use a speed increaser as the transmission 21.

  In addition, in the case of the drive assist device according to the second embodiment, there are many differences and types of the respective gears, and the change and adjustment can be performed in accordance with the pedaling force of the pedals 7a and 7b. Contribute to control. Since the speed increaser is relatively expensive, if it is not mounted, a combination of large and small types of each gear may be devised using a speed reducer. Even in such a case, power can be effectively generated.

  It should be noted that the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the technical scope of the present invention, and all technical matters included in the technical concept described in the claims are described. Is an object of the present invention. Each of the above embodiments shows a preferred example, but those skilled in the art can realize various modifications from the disclosed contents, and these are described in the appended claims. It is within the stated technical scope. For example, if the base (frame) is of a bifurcated type, the main parts of the drive assist device according to each embodiment, the guide members 10a and 10b, the variable mechanisms 9a and 9b, and a part of the variable mechanisms 9a 'and 9b' will be described. It is also possible to make a modification so as to be arranged inside the branch portion so as not to hinder the operation of the movable part.

  The drive assist device of the present invention can be used in a paddling boat used in a resort, a lake, a pond, or the like, a rickshaw, a rear car, a paddling toy, etc. installed in a resort, amusement park, an agricultural facility, a playground, or the like. Can be applied to

1a, 1a 'Head tube 1b Top tube 1c Down tube 1d Seat tube 1e, 1e' Seat stay 1f, 1f 'Chain stay 1g Front leg 1h Rear leg 2 Handlebar 2' Handle 3 Saddle 4 Front suspension 5 Front wheel 5a, 6a Rim 5b, 6b Tire 6 Rear wheel 7a, 7b Pedal 8 Support shaft 9a, 9a ', 9b, 9b' Variable mechanism 9a-1, 9b-1, 9a'-1, 9b'-1 Plate-shaped piece 9a-2, 9b -2, 9a'-2, 9b'-2 Movable piece 10a, 10b Guide member 11a, 11b Annular guide groove 12a, 12b Roller 13 First gear 14 Second gear 15 Third gear 16, 16 ', 16 "Fourth Gear 17 Fifth Gear 18 Insertion Shaft 19a, 19b Rack and Pinion 20a, 20b Fixed Piece Reference Signs List 21 transmission 22 power generation motor 23, 23 'support shaft 24 rotation shaft 25 weight 26 elongated hole 27 pin-shaped projection C1 first chain C2 second chain C3 third chain D1, D2 reinforcing member GO outer guide member L Land LB Reinforcement board LH Shaft hole T Tap V Slide groove

In order to solve the above technical problems, one embodiment of the present invention provides a support shaft rotatably supported on a base, a pedal that applies a rotational force to the support shaft, and a support shaft and a pedal attached to the support shaft. When movable, a variable mechanism capable of changing the distance between the support shaft and the pedal, and a guide member fixed to the base so as to face the variable mechanism by inserting the support shaft at an eccentric position, A transmission mechanism for transmitting the rotation of the support shaft to the transmitted portion, wherein the guide member is provided with an annular guide groove that extends in a non-circular and annular shape around the support shaft, and is variable. mechanism, have a movable engaging member along the wall portion of the annular guide groove, the annular guide groove, distortion and sharp end of the portion corresponding to portion corresponding to the front side blunt, the rear side of the substrate The support shaft is an annular guide in the guide member. Characterized in that it is inserted at a point inside the sharp end side closer.

Claims (6)

A support shaft rotatably supported on the base, a pedal that applies a rotational force to the support shaft, and a gap between the support shaft and the pedal when the support shaft and the pedal are attached and move. And a guide member fixed to the base so that the support shaft is inserted at an eccentric position so as to face the variable mechanism, and the rotation of the support shaft is transmitted to the transmitted portion. A transmission mechanism for transmitting, and a driving auxiliary device comprising:
The guide member is provided with an annular guide groove extending non-circularly and annularly around the support shaft,
The drive assist device, wherein the variable mechanism has an engaging body movable along a wall of the annular guide groove. The drive assist device according to claim 1,
The annular guide groove is a distorted annular shape having a blunt end at a location corresponding to the front side of the base and a sharp end at a location corresponding to the rear side,
The drive assist device, wherein the support shaft is inserted at a position near the acute end side of the guide member inside the annular guide groove. The drive assist device according to claim 2,
The drive assist device, wherein the annular guide groove has a rounded shape on the blunt end side, and an upper roundness on the blunt end side is smaller than a lower roundness. The drive assist device according to any one of claims 1 to 3,
In the variable mechanism, the support shaft is attached and fixed to a plate-like piece on one end side facing the guide member, and the other end side is partially engaged with a slide groove of the plate-like piece and faces the guide member. The movable piece is coupled to the plate-like piece so as to be movable along the slide groove in a shape sandwiching the plate-like piece, and is rotatable around the axis at a position on the outer other end side of the movable piece. The drive assist device, wherein the pedal is mounted, and the engaging body is mounted at a position on one inner side of the movable piece corresponding to between the support shaft and the pedal. The drive assist device according to any one of claims 1 to 4,
The transmission mechanism includes a first gear fixed to the support shaft, and a second gear fixed to a rotatable insertion shaft that is inserted behind the guide member of the base body and is rotatable. A first chain bridged between the first gear and the second gear; a third gear fixed to the insertion shaft so as to face the second gear; A fourth gear attached to and fixed to a support shaft of the unit, a second chain spanned over the third gear and the fourth gear, and a second chain attached to the support shaft. A drive assist device, comprising: a transmission for shifting rotational movement. A generator to which the drive assist device according to claim 5 is applied,
The transmission is a gearbox having the support shaft as a central axis,
A power generator comprising: a power generating means in which a fifth gear through which a third chain is bridged between the fourth gear and the fourth gear is fixed to a rotating shaft.

Images