JP2006347534A - Bicycle drive crank pedal angle advancing device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a bicycle drive crank pedal angle advancing device capable of reducing the invalid labor in the vicinity of a top dead center of a pedal when a bicycle travels, and having the function for enjoying the efficient and comfortable cycling. <P>SOLUTION: The bicycle drive crank pedal angle advancing device makes the angle advance of the top dead center of a pedal by dividing a crank shaft into right and left portions 5, 6, and connecting them to offset gears 7B, 7C on a coupling shaft 8, and offset gears 7A, 7D on the crank shafts 5A, 5B. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  TECHNICAL FIELD The present invention relates to a technical field related to a bicycle equipped with a function of causing the bicycle to travel forward by a human power when the lower pedal is at the bottom dead center and the upper pedal passes through the top dead center to advance forward. Belongs.

  The present invention relates to a drive device, a coupling device, and the like that contribute to improving the efficiency of human energy during bicycle travel.

  Conventionally, the improvement of the efficiency of the manpower energy of the bicycle has been mainly about the transmission, the chain changing transmission mechanism, the rear wheel hub internal transmission, and the weight reduction.

As described above, the conventional technology related to operation has been indifferent to the improvement of the speed change function, the reduction of the vehicle body weight, etc., and the ineffective part of the applied force is reduced or eliminated.
Therefore, the elderly, children, and ladies have been wasted. In conventional bicycles, when pedaling and running, the upper pedal is always at the top dead center when the lower pedal is at the bottom dead center.
Starting from here, when the downward linear motion is changed to a rotational motion, the energy use efficiency is poor and the loss increases near the top and bottom dead centers.
The normal driving of bicycles is that the crank-pedal is rotating with repulsive force and is currently unconsciously scooping, and the top dead center appears in the headwind, uphill, etc.
From year onwards, women are no longer able to move forward, and children are standing up and running.
Electric assist bicycles have also become widespread, but there are problems with inconvenience such as battery charging and travel distance.

In addition, the following patent documents 1, 2 etc. can be mentioned as a well-known and public technique relevant to this invention.
Japanese Patent Laid-Open No. 11-070889 Japanese Patent Laid-Open No. 06-263079

As described above, conventional bicycle driving techniques place emphasis on improving the shifting function, reducing the weight of the vehicle body, etc., and even those who normally run around the city casually pedal.
In addition, in the vicinity of the top dead center of the pedal, the current situation is that energy is lost by unconsciously converting labor into heat.

The present invention has been invented in view of the above points, and the present invention that achieves the above-described object is a bicycle drive crank pedal angle advancer, which improves the labor transmission efficiency near the top dead center of the upper pedal. The purpose is to make it possible to easily improve the power factor with a mechanism structure for improvement.
It is characterized by a pedal angle device that can be used as much as possible in order to save energy and make it easy to save energy while riding around the city and running around the city.

  In order to solve the above-described problems, the bicycle drive crank pedal advancing device according to the present invention solves the problem by using the following means.

That is, as described in claim 1 and claim 2, the bicycle drive crank pedal advancing device of the present invention that achieves the object bisects the crankshaft to the left and right, and rotationally drives the left and right shafts. In addition, the pedal angular advance device is characterized in that it is connected by a structure in which an angular gear is made variable, an eccentric gear having a shifted axis, and a mechanism.
An apparatus for achieving the object of claim 3 is provided.
A hollow chain sprocket shaft arranged on one side of the crankshaft via a gear is driven and rotated via a gear, with the shaft connected to the output shaft that is a combination of eccentric gears and an output shaft. It is a coaxial input / output device characterized by obtaining.

As described above, the present invention eliminates the consumption of reactive energy in the vicinity of the top dead center by causing the pedal on the opposite side to pass the top dead center and making it advance when one side of the pedal of the bicycle is at the bottom dead center. Moreover, comfortable travel can be achieved by reducing load fluctuations due to the bedal position during operation.
You can also start smoothly when you leave.
This is extremely effective for reducing unnecessary labor.

  DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of a bicycle drive crank pedal angle advancing device and bicycle according to the present invention will be described below with reference to the drawings.

  1 to 10 relate to an embodiment of the present invention, FIG. 1 is a schematic view of a bicycle, FIG. 2 is a perspective view of a pedal horizontal position, FIG. 3 is a perspective view of a pedal up and down position in an angular state, and FIG. Fig. 5 is a plan sectional view of the eccentric gear angular advancer, Fig. 5 is a schematic excerpt from the plane of the eccentric gear angular advancer, Fig. 6 is an eccentric gear angular advancer gear connection shaft diagram, and Fig. 7 is the main details of the eccentric gear. Figures 8 and 8 are chain sprocket hollow shafts, and Figure 9 is a two-part crank.

  In this embodiment, as shown in FIG. 2, the divided crankshafts 5A and 5B, the connecting shaft 8, the hollow shaft 9, the above four shafts, the crank arms 4A and 4B, the pedals 3A and 3B, and the eccentric gear 6A. , 6B, 6C, 6D, an eccentric spur gear (or a gear having an equivalent function when used in an eccentric gear), gears 7A, 7B, and chain sprocket 10 are configured as main components.

  FIG. 7 is a main detailed view of the eccentric gear 6 (A to D). The original center point P, the eccentric rotation shaft center point o, the eccentric amount W, the gear reference radius R, and the eccentric rotation maximum point H. , The eccentric rotation lowest point L.

  As shown in FIG. 6, the connecting shaft 8 has an eccentric direction of the eccentric gears 6B, 6C, 180 degrees out of phase and fixed to the shaft. The gears 7B, 6B, Are installed coaxially and integrated.

  As shown in FIG. 9, the split crankshafts 5A and 5B have eccentric gears 6A and 6D at their shaft ends, crank arms 4A and 4B at their opposite shaft ends, and the lowest point L in FIG. So that it is in the same direction as the crank arm.

FIG. 8 of a partial cross-sectional view of the chain sprocket is a diagram in which a gear 7A is fixed to one end of the hollow shaft 9 and a chain sprocket 10 is fixedly attached to the opposite end.

The integrated shafts, crankshaft, connecting shaft, and hollow shaft are arranged as shown in FIG.
The shaft centers of the split crankshafts 5A and 5B are arranged on the same line, and the crank arms are arranged horizontally and forward and rearward, with the phase changed by 180 degrees.
The phase relationship between the eccentric gears 6B and 6C of the connecting shaft 8 and the eccentric gears 6A and 6D of the crankshafts 5A and 5B is, as shown in FIG. The eccentric rotation lowest point L is arranged so as to mesh with each other.
The gear 7B of the connecting shaft 8 and the gear 7A of the hollow shaft 9 mesh with each other, and the crankshaft 5A passes through the hollow shaft.

  As shown in FIG. 4, the crankshafts 5 </ b> A and 5 </ b> B, the connecting shaft 8, and the hollow shaft 9 are each independently held by a bearing such as a bearing.

The above is housed in a case, and the crankshaft case 2 of the bicycle shown in FIG.

  7 and 10 will be used to explain the symbols and simple operation functions of the angle advancement device.

Definition of sign

A Eccentric rotation tooth angle conversion angle of eccentric gear 6A B Eccentric rotation tooth angle conversion angle of eccentric gear 6B C Eccentric rotation tooth angle conversion angle of eccentric gear 6C D Eccentric rotation tooth angle of eccentric gear 6D Conversion angle H Eccentric rotation highest point of eccentric gear L Eccentric rotation lowest point of eccentric gear K Eccentric gear rotation direction P Gear reference radius center point o Eccentric rotation center point of eccentric gear R Gear reference radius W Offset Amount of core gear (eccentric distance)
S = Intersection where the two gears mesh at the reference radius when the crank pedal is horizontal.
S + (subscripts A, B, C, D) = the rotational position of the S point of each eccentric gear when the crankshaft 5A rotates to the bottom dead center.

FIG. 10 is an assumption diagram in which the pedal 3A rotates 90 degrees from the pedal horizontal position to the bottom dead center.
That is, the eccentric gear 6A rotates around the center point o of the rotation center axis by ∠S o SA degrees until the gear initial mesh point S reaches SA.

When this rotation angle is converted into the opening angle of the reference radius center point P of the eccentric gear, ∠A degree = ∠SPSA degree.
Since S of 6A is the eccentric rotation maximum point H side, the distance So> SP, and ∠A degree> ∠So SA degree.
When viewed from the reference radius center point P of the eccentric gear, the difference between the original rotation angle of 90 degrees and ∠A is an element of the angular advance angle.

Since the eccentric gear 6B rotates in mesh with 6A, the eccentric gear 6B rotates by ∠A degrees when viewed from the reference radius center point P of the eccentric gear.
The rotated point is assumed to be SB.
Actually, since the rotation center point o of the eccentric gear rotates on the shaft, the initial meshing point S of the gear must rotate by ∠B = ∠S o SB = degree in order to reach the rotated point SB. .
Since S in 6B is the lowest eccentric rotation point L side, the distance So <SP.
Therefore, ∠A degree <∠B degree, and the difference is one element of the advance angle.

The eccentric gear 6C is directly connected to the eccentric gear 6B by the connecting shaft 8, and rotates by ∠B degrees around the rotation center point of the eccentric gear.
Thereafter, the eccentric gears 6C and 6D similarly repeat the rotation of the rotation center point o of the eccentric gear and the reference radius center point P of the shaft eccentric gear little by little. The angular advance angle reaching is the sum of the angular advance elements of each stage.
That is, the difference between the rotation angle ∠D degree = ∠S o SD degree of the counter pedal 3B and the initial rotation angle 90 degrees is ∠D degree−90 degrees.

A calculation example in which a numerical value is substituted for each gear is shown.
Each gear reference radius R = 15.75 mm.
Two of the above gears correspond to 7A and 7B.
Make the remaining 4 eccentric gears with eccentricity W = 1.5 mm,
Corresponding to 6A, 6B, 6C, 6D.
The calculation result of the angular advance angle 18 when the pedal 3A is pushed down to the bottom dead center as shown in FIG. 3 from the pedal position in FIG. 2; the angular advance angle 18≈21.5 degrees.
When the pedal is rotated with the above settings,
The reference radius of the meshing eccentric gear, the distance variation between the center points ≈ 0.15 mm.

Set as above,
The eccentric amount W of the eccentric gear may be small with respect to the gear reference radius R because the four-stage gear repeats the angular advance little by little. Can be suppressed to a practically acceptable one.

Moreover, the following can be mention | raise | lifted as a secondary utility.
The gear ratio changes due to the difference in radius between the eccentric gear main driving side and the driven side meshing point.
In FIG. 10, the eccentric gear radius ratio from the angular position pedal 3B ′ to the rotational horizontal position (between the two eccentric gear meshing points S and the eccentric gear main driving side o. The meshing point S and the driven side o ratio) is
It changes from 1: 1 to 17.25: 14.25≈1.2, and the gear ratio also changes with the reciprocal of the ratio.
Further, if the effective load fluctuation rate from the angular position pedal 3B ′ to the rotational horizontal position is (effective value / (effective value + invalid value)) * 100, it changes from 26% to 100%.
In the case of the pedal 3B ′, which is as low as 26% of the effective rate, the transmission ratio of the eccentric gear is approximately 1: 1, and labor is transmitted.
In the horizontal position where the effective ratio is as high as 1: 1, the speed is increased by approximately 1.2 times depending on the eccentric gear transmission ratio.
Therefore, the transmission change coefficient of force is
Transmission coefficient for horizontal pedal = 1 / 1.2 ≒ 0.83
Transmission coefficient at angular position pedal 3B '= 0.26 / 1 = 0.26
Then,
Transmission change coefficient = (Transmission coefficient at the time of the horizontal pedal / Transmission coefficient at the time of the angular position pedal 3B ′) = 0.83 / 0.26≈3.2.
Therefore, the amount of force applied is averaged, resulting in smooth running.
The operation from the horizontal position to the bottom dead center is the reverse of the above, but the effect on the force is the same for averaging and smoothing.

The conventional bicycle has a change from the top dead center with an effective rate of 0% to a horizontal position of 100%, and since the pedal and the chain wheel are directly connected, the transmission change coefficient is 100/0 = infinity. (The pedal does not rotate for a simple downward force at the top dead center), and the force is not smooth and wastes energy.

    Bicycle overview     Pedal horizontal position perspective view     Perspective view of the vertical position of the pedal in a square state     Eccentric gear angular advance device plan sectional view     Plane excerpt of eccentric gear angular advancer     Eccentric gear angular advancer gear connecting shaft     Eccentric gear main details     Chain sprocket hollow shaft     2-part crankshaft     Eccentric gear angular advance device calculation diagram

Definition of main part numbers

1 Bicycle body 2 Crankshaft case 3 (with subscript) Pedal 4 (with subscript) Crank arm 5 (with subscript) Crankshaft 6 (with subscript) Eccentric gear 7 (with subscript) Gear 8 Gear connecting shaft 9 Hollow shaft 10 Chain wheel 11-17 Bearing 18 Angular advance angle

Claims (3)

The bicycle drive crankshaft mechanism is characterized in that force is transmitted through a structure and a structure in which the drive crankshaft of the bicycle is divided into left and right and the peripheral speed is made variable on the separated shaft.   A pedal angle advancing device comprising: a mechanism and a structure having variable peripheral speeds according to claim 1 and a mechanism in which an eccentric gear having a shifted axis is combined.   The connecting shaft of the mechanism combining the eccentric gears with the shaft axis shifted according to claim 2 is used as an output shaft, and a chain sprocket output is obtained on the same shaft as the crankshaft through the hollow shaft. The same axis input / output device.

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