RU2228279C2 - Scooter - Google Patents

Abstract

FIELD: transport engineering. SUBSTANCE: invention relates to vehicles operated by man power. Proposed device contains frame with support for several humans, front and rear wheels, handlebar, foot drive 24.1, 24.2, 24.3, 24.4 and transmission formed by planetary gear mechanism and gear trains. Planetary gear mechanism has two sectional central wheels. Central wheel composed of wheels 1.1 and 1.2 is non-round. Sectional gear wheels 4.1-4.4 of other central wheel are secured on hollow coaxial shafts 6.1-6.4 forming sectional drive shaft. Carrier B is driven and provided with gear rims 9, 10 to transmit torque to rear wheel. Planet pinions are double-row. Planet pinions 2.1 and 2.3 engaging with non-round central wheel are round and they are eccentrically displaced relative to their axles 5.1, 5.3 through value of displacement of non-round central wheel and they have equal number of teeth with said wheel. EFFECT: compact multiplace vehicle capable of reducing energy losses for movement by using weight to provide uniform torque on drive wheel. 3 cl, 4 dwg

Description

The invention relates to transport engineering, and in particular to vehicles powered by the muscular strength of a person, and can be used as a compact collective and individual vehicle.

A vehicle is known (see RF patent No. 2094288 C1, B 62 M 1/20, 1999) containing a frame, a rear driving wheel, a front wheel, a steering wheel, elastic elements located symmetrically on both sides of the frame and having a supporting platform. The elastic elements are connected to the rear drive wheel by means of a transmission device.

The disadvantages of the known device are the use of elastic elements in the drive, the operation of which depends on the weight of the person and requires the use of additional deflection limiters and compensators, the difficulty of transmitting torque to the drive wheel.

A scooter is also known (see RF patent No.2009941 C1, B 62 M 1/00, 1994), containing a base resting on at least one drive wheel, a transmission with overrunning mechanisms, made in the form of a chain transmission for converting back and forth translational motion in the rotational motion of the drive wheels, with supporting platforms for legs with rollers mounted on them for movement on the base, and the transmission is parallel to the horizontal plane.

The disadvantage of the scooter lies in the inconvenient and unreliable drive with irrational pedaling techniques.

Of the known similar vehicles, the closest in technical essence is a passenger cycle car driven by the muscular strength of the legs, back, arms, weight of the driver and cargo (see RF patent No. 2144450 C1, B 62 M 1/04, 1999). The cycle car contains a front driven wheel, a steering wheel, a frame with two rear wheels located rigidly on the same axis, a drive and right and left drive levers made with a pedal platform along the entire length for the driver to move along it, connected to the beam via connecting rods and rear ends through a hub with the axle of the rear drive wheels and with a planetary gear. On the axis of the rear wheels there is a movable ring gear, which is both a gear housing and made with external oblique and internal straight teeth, with which it is connected to four satellites through a small gear, and the large gear of the satellite is connected through 4 intermediate satellites with a sun gear mounted on the axle splines rear wheels. At the ends of the levers are fixed spring-loaded dogs that engage with the external oblique teeth of the ring gear.

The disadvantages of the known design are the complexity and unreliability of the drive, as well as the use of a 3-wheel circuit.

The objective of the present invention is to create a compact multi-seat vehicle, which allows to reduce energy consumption for movement through the use of the body weight of the entire crew with obtaining uniform torque on the drive wheel.

The problem is achieved in that in a scooter-carriage containing a frame carrying supports for several people, a rear drive and front steered wheels, a steering wheel, an auxiliary handrail, a foot drive and a transmission formed by several mounted sequentially converting mechanisms, cylindrical and bevel gears, connected the intermediate shaft, according to the invention installed sequentially converting mechanisms made in the form of a planetary gear mechanism installed in the housing, and which has a variable gear ratio and two central wheels, one of which is fixed, offset from its axis of rotation and has a non-circular shape, and the other is made integral and formed by several gear wheels that are mounted on hollow coaxial shafts that form a composite drive shaft, at the other ends of which the drive levers are rigidly fixed, the carrier, which is a follower, having external gears for transmitting torque to the rear wheel through gears and a 2-row axle carrier x satellites meshed with the central wheels and providing a kinematic connection of each coaxial shaft with the carrier, while the meshed satellites and central wheels have the same number of teeth, and the satellites mated to a non-circular central wheel are round and eccentrically offset relative to their axes of rotation by the amount of displacement of the non-circular central wheel.

The non-circular central wheel is made integral and is formed by two non-circular gears rotated relative to each other by a phase angle, each of which is meshed with a group of satellites, providing a kinematic connection of each coaxial shaft with the carrier.

Each support for each crew member consists of a fixed part mounted on the frame for the heel of the foot and a movable pedal for the forefoot of the foot, mounted on the drive arm and oscillating during operation.

Such a constructive implementation of the scooter-crew will ensure the achievement of a given technical result due to the corresponding kinematic connections of the coaxial shafts with the drive levers fixed to them with the carrier of the planetary mechanism. The use of a gear with a non-circular central wheel with an average gear ratio of 1: 1 provides a cyclically changing gear ratio of the planetary gear. The use of a 1: 1 gear ratio for the second composite central wheel and the gears meshed with it provides the transformation of the oscillatory motion of the drive levers and gears forming the second composite central wheel and rigidly connected by coaxial shafts, relative to the middle position lying in the plane of the supports, into rotational drove the movement. The number of axes of 2-row satellites and their position determines the number of coaxial shafts forming a composite output shaft, the number of torque pulses transmitted to the carrier, and their phase shift. The use of a composite non-circular central wheel allows constructively solving the problem of obtaining a phase shift of pulses of 45 ° or less to increase the uniformity of torque on the carrier. The use of supports consisting of fixed parts mounted on the frame and movable pedals allows you to use the body weight of each crew member to create torque on the drive wheel by transferring it from one pedal to another. The presence of a fixed part allows you to relax when moving. Placing on the carrier several gear rims of external gearing allows you to stepwise change the gear ratio of the transmission from the drive to the drive wheel.

To explain the invention, a specific embodiment of the invention is provided below with reference to the accompanying drawings, in which:

figure 1 shows a General view of the scooter crew;

figure 2 shows the kinematic diagram of the transmission;

figure 3 shows 4 extreme positions of one 2-row satellite 2.1 and 3.1 relative to the center wheels 1.1 and 4.1;

figure 4 shows a diagram of the positions of the initial circles of the eccentrically displaced satellites relative to the non-circular central wheels for the case of installing on the carrier four axes of 2-row satellites.

The scooter crew (Fig. 1) contains a frame 16 that supports bearings 23.1, 23.2, 23.3, 23.4, a drive rear wheel 18, a front steered wheel 19, a steering wheel 20, an auxiliary handrail 21, a transmission 22, pedals 24.1, 24.2, 24.3, 24.4 .

The transmission (figure 2) contains a planetary mechanism mounted on the frame 16, having a housing 8, fixed non-circular central wheels 1.1 and 1.2, forming a composite non-circular central wheel 1, gears 4.1, 4.2, 4.3, 4.4, forming a second composite central wheel 4, rigidly mounted on the hollow coaxial shafts 6.1, 6.2, 6.3, 6.4, forming a composite drive shaft, at the other ends of which the drive levers 7.1, 7.2, 7.3, 7.4 with pedals 24.1, 24.2, 24.3, 24.4 are fixed. Axes 5.1, 5.2, 5.3, 5.4 of 2-row satellites 2.1 and 3.1, 2.2 and 3.2, 2.3, 3.3, 2.4, and 3.4 (axes 5.2 and 5.4 with satellites not conventionally shown) are fixedly mounted on the planet carrier planet carrier V and the gear rings 9 are fixed and 10, one of which is meshed with a block of gears formed by gears 11 and 12 mounted on the splines on the intermediate shaft 15, at the other end of which a bevel gear 13 is rigidly fixed, which is meshed with a gear mounted on the drive shaft 17 of the rear wheel wheel 14.

The device operates as follows.

The motion of the scooter crew from a stationary state is carried out by its dispersal by one or more crew members to a certain speed. In this case, the rotation of the rear wheel 18 (Fig. 1) through the shaft 17, bevel gears 14 and 13, the intermediate shaft 15 and one of the wheels 11 or 12 of the gear block is transmitted through the gear crowns 9 or 10 to the planet carrier B, which is movably mounted on the axes 51, 5.2, 5.3, 5.4 inform the eccentrically mounted round satellites 2.1, 2.2, 2.3, 2.4 of the rolling movement of the fixed composite non-circular central wheel formed by the gears 1.1 and 1.2 (FIG. 2). Running in eccentric satellites of a non-circular displaced central wheel causes their radial beats and, as a consequence, uneven rotation of their axes 5.1, 5.2, 5.3, 5.4 and the satellites 3.1, 3.2, 3.3, 3.4 and gears 4.1 engaged with them, rigidly fixed on them 4.2, 4.3, 4.4, forming a composite second central wheel. Figure 3 shows the extreme positions of the initial circles of one 2-row satellite 2.1 and 3.1 that arise when rolling in 4 relative to the central wheels 1.1 and 4.1.

The value of the gear ratio of the planetary mechanism (for ω ₁ = 0) is determined by the formula

where ω ₁ , ω _in , ω ₄ are the angular velocities of the non-circular central wheel 1.1, carrier B and the central wheel 4.1, respectively;

z ₁ , z ₂ , z ₃ , z ₄ - the number of teeth, respectively, of the Central wheel 1.1, the satellites 2.1 and 3.1, the Central wheel 4.1.

When the number of teeth of the gears in the gearing is equal and the eccentric displacement of the central wheel 1.1 and satellite 2.1 is equal, the instantaneous gear ratio

where r $\genfrac{}{}{0ex}{}{\text{''}}{\text{1}}$ , R $\genfrac{}{}{0ex}{}{\text{''}}{\text{2}}$ - instantaneous values of the radii of the non-circular central wheel 1.1 and the eccentric satellite 2.2 at the point of contact.

определяет мгновенное значение передаточного отношения и его знак.Ratio

determines the instantaneous gear ratio and its sign.

т.е. скорость центрального колеса ω₄=0.At

those. the speed of the central wheel ω ₄ = 0.

передаточное отношение положительно, направления вращения водила В и центрального колеса 4.1 одинаковы.At

the gear ratio is positive, the directions of rotation of the carrier B and the central wheel 4.1 are the same.

передаточное отношение отрицательно, направления вращения водила В и центрального колеса 4.1 различны.At

the gear ratio is negative, the directions of rotation of the carrier B and the central wheel 4.1 are different.

The instantaneous gear ratios have maximum values when the difference between the instantaneous radii R $\genfrac{}{}{0ex}{}{\text{''}}{\text{1}}$ -R $\genfrac{}{}{0ex}{}{\text{''}}{\text{2}}$ = ± 2e, where e is the displacement.

For upper position: R $\genfrac{}{}{0ex}{}{\text{''}}{\text{1}}$ -R $\genfrac{}{}{0ex}{}{\text{''}}{\text{2}}$ = -2e - the rotation speed of the central wheel ω _{4 is} maximum and has the same direction with the carrier.

For lower position: R $\genfrac{}{}{0ex}{}{\text{''}}{\text{1}}$ -R $\genfrac{}{}{0ex}{}{\text{''}}{\text{2}}$ = 2e - the rotation speed ω _{4 is} maximum and opposite to the direction of rotation of the carrier.

For lateral positions: R $\genfrac{}{}{0ex}{}{\text{''}}{\text{1}}$ = R $\genfrac{}{}{0ex}{}{\text{''}}{\text{2}}$ rotation speed ω ₄ = 0.

The rotation of the carrier B and the axis 5.1 with the satellites 2.1 and 3 1 from the lateral position to the top by an angle α causes an accelerated rotation of the central wheel 4.1 with a positive sign to the maximum value. The rotation of the carrier by an angle φ from the upper position is accompanied by a decrease in the rotation speed of the central wheel 4.1 to zero. A further rotation of the carrier by an angle of 2β is accompanied by a change in sign to negative and an increase in the rotation speed of the central wheel 4.1 to a maximum value in the lower position and a decrease to zero in the lateral. The alternating rotation of the central wheel 4.1 through the shaft 6.1 causes an oscillatory movement of the drive arm 7.1 mounted on this shaft relative to the middle position located in the plane of the bearing pads 23.1 (Fig. 1). The rotation of the remaining satellites and the central wheels meshed with them occurs similarly with a phase shift determined by the position of the axes 5.1, 5.2, 5.3, 5.4 on carrier B and the rotation angle φ of the central wheels relative to each other. Figure 4 shows the position of the initial circles of the eccentric satellites 2.1, 2.2, 2.3, 2.4, corresponding to the location of the four axes on the carrier through 90 °. Non-circular central wheels 1.1 and 1.2 are rotated by a phase angle φ = 45 ° relative to each other. As a result, the uniform rotation of the carrier is converted into the oscillatory movement of the drive levers with a phase shift of 45 °. Synchronous transfer of body weight from the supporting platform to the pedal (from the heel to the toe) starting to lower, and from one part of the lever to the other, causes torque pulses to the carrier. In the braking mode, the effects on the pedals are reversed. The magnitude of the momentum of the torque depends mainly on the applied load on the pedal, the magnitude of the eccentricity e, the efficiency of the planetary mechanism, which varies widely and is very low (less than 0.01) for the positions of the satellites corresponding to very large gear ratios (lateral positions of the satellites on figure 3). The increase in the number of impulses of torque per one revolution of the carrier by installing several sequentially working converting mechanisms allows to increase the uniformity of torque and efficiency of the entire device. The rigid kinematic connection of the transmission and drive levers ensures the synchronous operation of the crew. When moving by inertia and to rest when moving, body weight is transferred to the supporting platforms.

Claims (3)

1. Scooter-crew, containing a frame bearing supports for several people, rear-wheel drive and front-steered wheels, steering wheel, auxiliary handrail, foot drive and transmission formed by several successive converting mechanisms, cylindrical and bevel gears connected by an intermediate shaft, characterized the fact that installed sequentially converting mechanisms are made in the form of a planetary gear mechanism installed in the housing having a variable gear the ratio and two central wheels, one of which is fixed, is offset from its axis of rotation and has a non-circular shape, and the other is made integral and is formed by several gear wheels that are mounted on hollow coaxial shafts that form a composite drive shaft, at the other ends of which drive wheels are rigidly fixed levers, carrier, which is driven, having gears of external gearing for transmitting torque to the rear wheel through gears and bearing axles of 2-row satellites located in the gear lyze with the central wheel and providing a kinematic connection of each shaft coaxial with the carrier, the meshing pinion gears and the central wheels have the same number of teeth, and the satellites associated with non-circular central wheel, have a circular shape and are eccentrically offset relative to their axis of rotation by the amount of displacement of the non-circular central wheel. 2. The scooter crew according to claim 1, characterized in that the non-circular central wheel is made integral and formed by 2 non-circular gears rotated relative to each other by a phase angle, each of which is engaged with a group of 2-row satellites, providing kinematic connection of each coaxial shaft with a carrier. 3. Scooter-crew according to claim 1, characterized in that each support for each crew member consists of a fixed part mounted on the frame, for the heel of the foot and a movable pedal for the forefoot, mounted on the drive arm and oscillating during operation traffic.

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