WO2009137905A1

WO2009137905A1 - Bicycle with a sliding seat

Info

Publication number: WO2009137905A1
Application number: PCT/BY2009/000005
Authority: WO
Inventors: Александр Васильевич СИНИЛО
Original assignee: Sinilo Alexandr Vasilievich
Priority date: 2008-05-14
Filing date: 2009-04-20
Publication date: 2009-11-19

Abstract

The invention relates to two-wheel human-powered bicycles. The inventive bicycle comprises front and rear wheels, a front fork, a handle bar and a frame. A seat slider is mounted on a guiding frame so as to slide therealong. The drive cranks with pedals are parallel and unidirectional or are close to said position. A driving chain wheel of the drive is designed in such a way that the straight line segments, connecting the centers of the tooth roots, form a convex polygon, the length of the sides of which is equal to or a multiple of the chain pitch, or the driving pulley of a notched belt drive is designed in such a way that the smooth closed pitch curve of the teeth (along a cord line axis), i.e., the frontier of a convex set, or the driving pulley of the drive is designed in such a way that the cross-section profile is enclosed by the closed curve, i.e., by the frontier of a convex set. Coordinated cyclic efforts of the hands, legs, back and abdominal muscles of a cyclist are sufficient for the uniform run-off of a flexible element from the driven chain wheel or the pulley of the bicycle drive. Said efforts are carried out in such a way that the angular velocity of the crank rotation increases when the distance between the carriage axis and the point at which the flexible element runs on the driving chain wheel or pulley of the drive is decreased, and decreases when said distance is increased. The transmission ratio between the crank and the wheel is automatically changeable according to the crank position.

Description

Academic bike. 1. The area of technology.

The invention relates to bicycles driven by human muscular power. 2. The prior art. The applicant knows the closest analogue of the claimed invention:

The prototype of the claimed invention is a bicycle [1]. He is closest to him in the aggregate of essential features. It contains the front wheel in the front fork. Its shaft and steering wheel are rotatably connected to the frame. It has a rear wheel. The seat slider is mounted movably along the frame guide. The parallel and one-way cranks from 20 cm to 50 cm long are connected to the axis of the drive carriage. Pedals with foot mounts.

The cyclist applies maximum effort to the pedals on the arc of the path, where the position of the crank changes from upward to horizontal. Therefore, the flexible member unevenly disengages from the driven sprocket or drive pulley. This is his flaw. 3. Disclosure of the invention.

The problem to which the invention is directed, is that for uniform descent of the flexible element from the driven sprocket or pulley of the bicycle drive, there should be enough coordinated cyclic efforts of the cyclist's arms, legs, back and abdominals.

The technical result of the invention is a bicycle with a drive sprocket or drive pulley, automatically changing the gear ratio between the crank and the wheel, taking into account the position of the crank, for the uniform descent of the flexible element from the driven sprocket or drive pulley, which is sufficient for the cyclical coordinated efforts of the cyclist's arms, legs, back and abdominals.

The aforementioned task is achieved in that the bicycle, comprising the front and rear wheels, the front fork, the steering wheel, the frame, the seat slider, mounted to move along the frame guide, the pedals with the foot fasteners, is equipped with cranks directed so that the dihedral angle passes along the axis of the carriage with an edge, one face of which contains a beam from a point on the axis inside the hole in the left crank for the axis of the carriage, passing through a point on the axis inside the hole in the same crank for the pedal axis, and the other face contains the same learning in the right crank, - not more than 20 °, the length of which is not limited to from 20 cm to 50 cm, with a drive sprocket made of such a shape that, connecting the centers of the depressions, the straight lines form a convex polygon with a side length equal to or a multiple of the pitch a chain, or a drive-belt drive pulley of such a shape that is a multiple of the step of the toothed belt, containing points defining the position of the interdental cavities, a dividing smooth closed curve of the teeth (along the axis of the cord) is the boundary of the convex set, or you a drive pulley filled with such a shape that the section profile with a plane perpendicular to the axis of the shaft hole passing through the middle of the pulley’s working surface is bounded by a closed curve — the boundary of a convex set. The middle of the working surface of the pulley is the middle of the surface of the pulley in contact with the surface of the flexible drive. The gear ratio between the crank and the wheel automatically changes taking into account the position of the crank. For uniform descent of the flexible element from the driven sprocket or the pulley of the bicycle drive, the coordinated cyclic efforts of the cyclist's arms, legs, back and abdominal press are sufficient. Applied so that the angular speed of rotation of the cranks increases if the distance from the axis of the carriage to the point where the flexible element runs onto the drive sprocket or drive pulley decreases, and decreases if the distance increases. 4. A brief description of the drawings.

Figure 1 is a front view of an example of a better embodiment of the invention; in FIG. 2 is an example of constructing a profile of a depression with an offset of arcs; in FIG. 3 - an example of the construction of the profile of the depression without offset arcs; figure 4 is an example of constructing a trapezoidal profile of the interdental cavity of the pulley; figure 5 is an example of building an AT profile of the interdental cavity of the pulley; figure 6 is an example of constructing a profile of the cavity for the gear chain; in FIG. 7 - the first phase of the cyclical movement of the cyclist; in FIG. 8 - the second phase; in FIG. 9 - the third phase; in FIG. 10 - the fourth phase. δ. Best Mode for Carrying Out the Invention. An example of a better embodiment of the invention is a bicycle (FIG. 1). It contains front and rear wheels, front fork, steering wheel, seat slider, frame. The frame guide is perpendicular to the vertical line passing through the center axis of the carriage. Two parallel and one-sided cranks are connected to the axis of the drive carriage. Pedals with foot mounts. The path line of the seat touches the path of the pedal axis. The centers of the hollows of the drive sprocket lie on arcs circles whose centers are located at the vertices of the rhombus. 6. Industrial applicability. The profile of the cavity with offset arcs (figure 2) of the drive sprocket of the drive for roller or sleeve chains at a given center, the diameter of the meshing element of the chain D ₄ and two adjacent centers of the troughs, for example, is constructed as follows. The center of the depression is connected by line segments with two adjacent ones. The length of the segment is the chain pitch t. Perpendiculars to the midpoints of the segments are drawn. The first case is that the perpendiculars intersect. Q is the intersection point. The value of the parameter z shows how many times the angle between the perpendiculars is less than the full. The geometrical characteristic of the engagement λ, the diameter of the pitch circle d _d and the diameter of the circle of the protrusions D _e are [2]: λ = t / D,;

180 °. d _d = t cos her, z

1 RΩ ° D _e = t (K + ctg -), z where the tooth height coefficient K is determined from the table [2] λ from 1, 40 from 1, 50 from 1, 60 from 1, 70 from 1, 80 to 1, 50 to 1, 60 to 1, 70 to 1, 80 to 2.00 K 0.480 0.532 0.555 0.575 0.565

An arc of a dividing circle with a center in Q and a diameter d _{d is} drawn through the center of the depression. The displacement of the centers of the arches of the depressions e is calculated from [2] e = 0.03 /.

From the center of the cavity at a distance of [2] 0.5e, the point O ^'is marked on the pitch circle. Trench radius g and half the angle of the depression α are calculated according to [2]: g = 0.5025D _c + 0.05mm \

Α = 55 ° - ^.

Z

An arc of radius r is drawn from point O ^' . The position of point E on the arc is determined by the angle α. The conjugation radius η and the conjugation angle β are calculated from [2] r, = 0, SD ₄ + r = 1.3025D ₄ + 0.05mm \

Z

A line is drawn from point E through point O ^' . The radius η is plotted on it, with which the arc EF is drawn from the center O _x , determined by the angle β β _÷ Then a straight line is drawn .... ... _. length of profile FG [2]

FG = D _c (1.24 sip φ - 0.8 sip β),

where ^ = 17 ° -—, z is tangent to an arc of radius r at point F.

The radius of the tooth head r _{2 is} calculated by [2] r ₂ = D _c (1.24 cos φ + 0.8 cos β - 1.3025) - 0.05 l.

A straight line is drawn from point G perpendicular to FG. It marks the radius r ₂ , which outlines from the center O ₂ , starting from point G, the tooth head to the intersection with point K of the circumference of the protrusions of diameter D _e with center in Q.

The second case - perpendiculars are parallel. The value of the parameter z is 10000000. The arc of the dividing circle is the side of the polygon. The arc of a circle of protrusions is a straight line outside the polygon parallel to the side of the polygon at a distance of half a chain pitch from it. Calculations and constructions are carried out in the same order and according to the same formulas as in the first case.

The least distant, located on opposite sides of the perpendicular, a pair of points of intersection of the tooth profile and the arcs of the circumferences of the protrusions is connected by a straight line segment. Constructing a profile of a depression without shifting the centers of arcs

(FIG. 3) is performed in a similar manner, but e = 0 is assumed.

The profile of the interdental cavity of the drive belt drive pulley (Fig. 4) and (Fig. 5) for a predetermined, containing points defining the position of the interdental cavities, a dividing smooth closed curve of the teeth (along the axis of the cord) 1, for example, is constructed as follows. At each point of this curve, the radius of curvature p is calculated. At a distance of Δ-0.5k, the point is marked normal inward, where Δ is the distance from the axis of the cord to the inner surface of the belt; k is the correction for the diameter of the tooth tips [3] 2p, mm to 50 to 78 to 118 to 198 to 318 to 500 k, mm 0.08 0.10 0.12 0.13 0.15 0.18.

The set of points obtained in this way forms the outer curve of teeth 2. At a distance of Δ-0.5k + / g _s from the point determining the position of the interdental cavity, point A is marked along the normal inward, where h _i is determined from the table if the HTD profile [3]

Designation h _s , mm r ₃ , mm r ₄ , mm mЗ 4.05 ± 0.20 1, 1 ± 0.10 2.65 ± 0.20 m4 5.05 ± 0.20 1, 3 ± 0.10 3.65 ± 0.20 m5 6.05 ± 0.30 1, 6 ± 0.15 4.7 ± 0.30

ЗМ 1, 2 ± 0.10 1, 2 ± 0.10 1, 0 ± 0.10

5M 2, 1 ± 0.15 1, 7 ± 0.15 1, 6 ± 0.15

8M 3.4 ± 0.20 2.0 ± 0.15 2.6 ± 0.20

14M 6.1 ± 0.30 2.5 ± 0.20 4.5 ± 0.10 if the trapezoidal profile [3] Determine- Size, Section dimensions, mm parameter designation S _s h _s r ₅ r ₆ 2Д °

1.0 1.0 ± 0.10 1.3 ± 0.10 O.Z ± O.YU O.Z ± O.YU 50 ± 2

1.5 1.5 ± 0.15 1.8 ± 0.15 0.4 ± 0.10 0.4 ± 0.10 50 ± 2 2.0 1.8 ± 0.15 2.2 ± 0, 15 0.5 ± 0.10 0.5 ± 0.10 50 ± 2

3.0 3.2 ± 0.20 3.0 ± 0.20 0.7 ± 0.10 1.0 ± 0.10 40 ± 2

OST m 4.0 4.0 ± 0.20 4.0 ± 0.20 1.0 ± 0.15 1.3 ± 0.15 40 ± 2

5.0 4.8 ± 0.20 5.0 ± 0.20 1.5 ± 0.15 2.0 ± 0.15 40 ± 2

7.0 7.5 ± 0.30 8.5 ± 0.30 2.5 ± 0.20 3.0 ± 0.20 40 ± 2 10.0 11.5 ± 0.3012.5 ± 0.30 3.0 ± 0.30 3.5 ± 0.30 40 ± 2

MXL 0.84 ± 0.100.69 ± 0.100.13 ± 0.050.25 ± 0.0540 ± 2

XL 1, 32 ± 0, 151, 65 ± 0, 150.64 ± 0.050.41 ± 0.0550 ± 2

L 3.05 ± 0.202.67 ± 0.201, 17 ± 0, 101.19 ± 0, 1040 ± 2 SO t _p H 4.19 ± 0.203.05 ± 0.20 1.6 ± 0.15 1.6 ± 0.15 40 ± 2 XH 7.9 ± 0.304.14 ± 0.302.39 ± 0.201.98 ± 0.2040 ± 2

XXH 12.17 ± 0.310.31 ± 0.33.18 ± 0.203.96 ± 0.2040 ± 2

T2.0 0.6 ± 0.05 0.8 ± 0.05 0.2 ± 0.05 0.2 ± 0.05 40 ± 2

T2.5 0.9 ± 0.10 1.0 ± 0.10 0.3 ± 0.05 0.2 ± 0.05 40 ± 2

DIN t _p T5 1.5 ± 0.151.95 ± 0.15 0.6 ± 0.05 0.4 ± 0.05 40 ± 2 T10 3.4 ± 0.20 3.4 ± 0.20 0.8 ± 0.10 0.6 ± 0.05 40 ± 2

T20 7.0 ± 0.30 6.0 ± 0.30 1.2 ± 0.10 0.8 ± 0.10 40 ± 2 if AT profile [3] Designation s _s , mm h _s , mm r ₅₁ mm r _6I mm 2β °

AT5 2.5 ± 0.151.95 ± 0.15 0.6 ± 0.05 0.4 ± 0.05 50 ± 2 AT10 5.0 ± 0.20 3.4 ± 0.20 0.8 ± 0, 10 0.6 ± 0.05 50 ± 2

AT20 10.0 ± 0.30 b.O ± O. O. 1.2 ± 0.10 0.8 ± 0.10 50 ± 2

In the case of constructing a trapezoidal profile (figure 4), point A is the middle of a segment of a perpendicular normal of length S ₅ .

Straight lines are drawn through the ends of this segment at an angle d to the normal. The radius of conjugation of lines with the segment S ₄ - r ₆ . And with an external tooth curve - r ₅ .

In the case of constructing an HTD profile (Fig. 5), point A lies on an arc of a circle of radius r ₄ centered on the normal. The radius of conjugation of this arc with the outer curve of the teeth r _b .

For a toothed chain, the center of the trough on the drive sprocket is the center of the roller on the chain sprocket. For a given center and two adjacent centers of the troughs, the profile of the part of the drive wheel with the trough (Fig.6), for example, is constructed as follows. The center of the depression is connected by line segments with two adjacent ones. On the segments are the tops of the teeth. The length of the segment is the chain pitch t. The tooth height h _x and the distance from the intersection point of the working faces to the top of the tooth C _{1 are} determined by the chain pitch t and according to the table [4] t (mm) 12.7 15.87 19.05 25.4 31, 75 L, (mm ) 8 9.75 11.5 15 19.5

C, (mm) 21 25.75 30.5 42.0 52.5 Perpendiculars are drawn to the midpoints of the segments. On the perpendiculars inward, the points of intersection of the working faces at a distance of C ₁ from the midpoints of the segments are marked. Two rays are drawn from these points at an angle of 30 ° to the perpendiculars, which determine the position of the working faces of the depression. From the working face of one tooth at a distance of the height of the tooth from the top of the adjacent tooth, a beam is drawn parallel to it until it intersects with the same beam starting on the second working face of the cavity. If these rays are parallel, then until they intersect with the second working face of the cavity. The distance h from the center axis of the carriage of the racing bike to the center of the surface of the seat for a given height of the cyclist is determined according to the table [5]

Height (cm) 160 165 170 175 180 185 190 190 h (cm) 63.1 66.0 68.8 71.7 74.6 77.5 80.4 The value of h is calculated by the formula [5] h = 13.667 + 0.697M, where M is the length of the leg (from the floor to the pubic bone) in centimeters. The distance H from the pedal to the center of the surface of the seat with a connecting rod length of 17 cm is

H = h + 17 cm.

In the plane perpendicular to the axis of the carriage containing the axis of the front fork shaft, a rectangular Cartesian coordinate system OXY is introduced as follows. Point O on the axis of the carriage. The axis OX is parallel to the guide. The positive direction of the OX axis coincides with the direction of travel of the bike. OY axis points up. The trajectory of the seat surface lies on the line y = T.

One of the conditions for pedaling is H≥R + | T | + 1cm, where R is the length of the crank.

Another condition for pedaling: the distance from the center of the seat to the pedals should be at least 0.5H. For | T | <0.5H + R, we estimate the shortest path length for the center of the seat.

The point of greatest distance from the OY axis of the center of the seat moving along the path of the smallest length has the coordinates

When the legs are extended and the pedals are at the farthest point from the guide point, the center of the seat is at point B with coordinates

, T).

ANGLE BETWEEN THE AXIS OX AND DIRECT IN

Lying outside the segment BO, the point C of the intersection of the line BO and pedal trajectory, has coordinates (Rсosμ, Rsiпμ).

When the legs are extended and the pedals are at point C, the center of the seat is located at point D with coordinates (d, T) satisfying the equation: (d-Rcosμ) ² + (T-Rsinμ) ² = H ² , d = RсОSμ - _d / H ² - (T -Rsiпμ) ² ,

Point D is the point of least distance from the OY axis of the center of a seat moving along the path of the smallest length. Assessment of the smallest length of the trajectory of the seat has the form:

If the height of the cyclist is 185 cm, N = 94.5 cm, L = 65.7 cm - an estimate of the shortest path length of the seat at T = 38 cm and R = 50 cm, and L = 26.1 cm at T = 35 cm and R = 35 cm. Therefore, to perform a full revolution of the pedals, in many cases the location of the guide relative to the axis of the carriage and the length of the cranks, you can only move on the seat along the guide. We assume that the cyclist moves along the guide during pedaling. We describe the method of pedaling, in which the flexible drive element evenly descends from the driven sprocket or pulley.

A cyclist sits on the seat. Holds the steering wheel with his hands. Having fastened his legs on the pedals, he makes cyclic movements with his legs, arms, back and abdominals. Each cycle has four phases. The first phase (Fig. 7) is the seat at the rear of the bike. Hands are straight. Legs are tightened by themselves, pedals moving up. In the first half of the phase, the back bends. The seat, moving backward, slows down, and in the middle of the phase stops in the extreme position. In the second half of the phase, the back straightens. The seat moves forward with acceleration. The second phase (Fig. 8) - the seat moves forward. The back is straightened. Hands bend at the elbows. The pedals move forward. At the beginning of the phase to its middle, the legs are tightened under themselves. From the middle of the phase, the legs bend at the knees. The third phase (Fig. 9) is the seat in the forward position. The back is straight. Hands are bent at the elbows. The legs are bent at the knees. The pedals move down. In the first half of the phase, the seat, moving forward, slows down, and in the middle of the phase stops in the extreme forward position. In the second half of the phase, the seat moves backward with acceleration. The fourth phase (Fig. 10) - the seat moves back. The back bends. Hands are straightened. The pedals move back. In the first half of the phase, the legs bend at the knees. In the middle of the phase, their vertical movement stops, and the cyclist begins to squeeze them under him.

Movements are made so that the angular speed of rotation of the cranks increases if the distance from the axis of the carriage to the point of incidence of the flexible element on the drive chain wheel or pulley decreases, and decreases if the distance from the axis of the carriage to the point of incidence of the flexible element on the drive chain or pulley decreases drive. Information sources:

1. Application for invention WO 2006/119601 A1.

2. GOST 591-69, p. 2-5.

3. Bakhanovich A. G., Skoibeda A. T. “Three-variable transfers”, Mn., 2005, p. 330-332. 4. Acherkan H. S. "Reference book of a machine builder)), vol. 4, pr. II M., 1963, p. 482.

5 ^. Timoshenkov V.V. “Installing a rational bike ride. Cycling Yearbook _{M. ,} 1985, p. 44-45.

Claims

Claim.

A bicycle containing a front wheel in the front fork, the shaft of which and the handlebar are rotatably connected to a frame in which the rear wheel is mounted, a seat slider mounted to move along the frame guide, connected to the axis of the drive carriage by cranks with pedals with means for attaching legs, characterized in that the cranks are directed so that a dihedral angle with an edge passing along the axis of the carriage, one face of which contains a ray from a point on the axis inside the hole in the left crank for the axis of the carriage, passing through a point on the axis inside the hole in the same crank for the pedal axis, and the other side contains a beam from a point on the axis inside the hole in the right crank for the carriage axis, passing through a point on the axis inside the hole in the same crank for the pedal axis - no more 20 °, the length of which is not limited to from 20 cm to 50 cm, the drive sprocket of the drive is made in such a way that the straight segments connecting the centers of the depressions form a convex polygon with a side length equal to or a multiple of the chain pitch, or a drive pulley of a toothed-belt drive fulfilling such a shape that the length of a multiple of the step of the toothed belt containing the points determining the position of the interdental cavities, the dividing smooth closed curve of the teeth (along the axis of the cord) is the boundary of the convex set, or the drive drive pulley is made in such a way that the section profile is a plane perpendicular to the axis of the hole for the axis of the carriage passing through the middle of the working surface of the pulley, it is limited by a closed curve - the boundary of a convex set.