RU2493998C1 - Unit for displacement in space with displacement accelerator that transforms shaft rotation in translation - Google Patents

Abstract

FIELD: transport.

SUBSTANCE: invention relates to devices that covert unit shaft rotation in translation of unit case over the surface. Proposed device comprises the case to house rotary shaft with lever with weight secured thereat, parallelogram-type travel accelerator, two pulsators and flexible linkage. Said accelerator one end is articulated at rotary shaft axle and another end articulated with weight axle. Flexible linkage coupled pulsators with weight rollers. Linkage one end is secured to rotary shaft and another end coupled with accelerator axle.

EFFECT: expanded range of motion speed variation, higher reliability.

5 dwg

Description

The invention relates to means that transform for moving in space the kinetic energy of a rotating shaft into the translational movement of the device by using the inertia forces of the mass of the load rotating together with the shaft. Such devices are able to move on the surface of various environments, in water and in air. Various technical solutions are known in the art which describe devices that convert one form of energy to another.

A patent has recently become known that describes a method and device for converting the kinetic energy of a rotating shaft into the translational motion of a vehicle body by using the inertia forces of the mass of a cargo rotating together with the shaft [1]. Such devices for moving in space can be made in various forms and forms: a vehicle on wheels, on sliding surfaces, in the form of a flying saucer, etc. [2], [3].

Closest to the claimed invention and adopted as a prototype is a device for moving in space that converts the kinetic energy of a rotating shaft into a controlled translational movement of the vehicle [2]. This device comprises a rotation shaft in the housing, on which a lever is fixed rigidly with a load freely moving on it, held by an annular flexible connection, which transmits energy pulses to the housing as a result of converting its interaction forces with the pulsator and the load. By changing the position of the pulsator relative to the axis of the rotation shaft, the device is given directional movement in space.

This device requires further improvement in terms of ensuring operational reliability of the ring flexible communication, smoothness and increase the speed of translational motion. In this regard, the technical task was set to develop and create a device in which the problem of converting the energy of a rotating shaft into translational motion more smoothly, with a large effect of converting one type of energy to another, was solved.

In addition, the task was to expand the range of changes in translational speed, increase traction and ensure high operational reliability of the main moving structural elements.

The solution to this problem is reflected in the claimed invention "Installation for moving in space with a stroke accelerator, converting the kinetic energy of a rotating shaft into translational motion."

The essence of the claimed device is presented in graphic materials and photographs.

Figure 1 presents a General view of the installation with the accelerator;

figure 2 - diagram of the translational movement of the rotating shaft during compression of the parallelogram acceleration mechanism to the axis of the load;

figure 3 is a diagram of the forces acting on the installation at the time of collision of flexible communication with the pulsator;

figure 4 is a General view of the current installation model on an open moving platform;

figure 5 - current model of the vehicle with the installation of accelerated motion on smooth supports.

The space-moving installation shown in Fig. 1 comprises a housing 14 with a rotation shaft 1 located therein, a lever 2 with four smooth rods, freely moving perpendicular to the rotation shaft in the slots of the bracket 9, rigidly mounted on the shaft 1, a parallelogram mechanism 3, consisting of three sections, hinged at one end on the shaft 1, the other - on the axis 5 of the load 4, rigidly mounted on the end of the lever 2, two pulsator 8 mounted on the housing 14 with the possibility of their movement relative to the axis of the rotation shaft 1 for measuring Changing the direction of traction. The axis 11 of the parallelogram mechanism 3 is installed in two sliders 7 that move freely along the rods of the lever 2. On the protrusions 15 of the connecting bracket 10 mounted on the lever 2, parallel threads of the flexible coupling are fixed at one end 6. Other ends of the flexible coupling, covering pulsators 8 and rollers 13 on the axis 5 of the load 4, rigidly fixed at the ends of the axis 11 of the section of the parallelogram mechanism 3. The axis of the pulsators 8, rollers 13 and the drive shaft 1 are parallel.

Presented in figure 2, the operation diagram of the mechanism 3 discloses the process of accelerating the translational motion of the installation casing 14.

Presented in figure 3, the diagram of the action of forces during operation of the installation justifies the process of converting the kinetic energy of rotation of the shaft 1 into the accelerated translational motion of the housing 14 of the installation.

Figure 4 presents the current installation model with the acceleration mechanism.

Figure 5 presents the current model of the vehicle with the installation that converts the kinetic energy of the rotating shaft into accelerated translational motion, on three smooth supports.

Installation that converts the kinetic energy of a rotating shaft into accelerated translational motion works as follows.

In some way (in the claimed invention is not disclosed) give rotation to the shaft 1 of the device (figure 1), placed in the housing 14.

Moreover, as engines for rotating the shaft 1, both mechanisms with internal combustion devices, and those operating on nuclear fuel or from batteries that accumulate energy from solar panels, and others, can be used. Synchronously with the rotation shaft 1, the lever 2 rotates with the load 4, a parallelogram acceleration mechanism 3 and a flexible coupling 6. The lever 2 can freely move in the slots of the bracket 9, rigidly mounted on the shaft 1. Rotating with the lever 2, the mechanism 3 and the flexible coupling 6 are always in tension under the action of the inertia force F _and acting on the load 4 of mass m ₁ .

With each revolution of the shaft 1, the flexible coupling 6, colliding with the pulsator 8, transfers the force T ₁ to the axis 11 of the parallelogram mechanism 3, using the roller 13 on the axis 5 of the load 4, as a "fixed block" (figure 1).

Under the action of the force T _{1, the} axis 11 moves to a distance l to the axis 5 of the load 4, held by the inertia force F _and , which leads to compression of the parallelogram mechanism and the translational movement of the shaft 1 with the housing 14 by a distance L (figure 2). The travel distance L is directly dependent on the number of sections of the parallelogram mechanism 3 and with sufficient shaft power can reach significant values:

L = k

where k is the number of sections,

l is the movement of the axis 11 of the first section (figure 2).

The speed of movement of the installation depends, respectively, on the number of sections, since the time interval for the movement of all axes of the parallelogram mechanism is the same:

V = k

where v is the velocity of the axis 11.

The tension force of the flexible connection thread T ₂ attached to the protrusion 15 of the bracket 10 (point K, FIG. 3) creates an additional force of movement of the installation, acting through the lever 2 on the load 4 in the positive direction of the coordinate axis X:

T _2X = T ₂ Cosα.

The force T _A (Fig. 3) arising on the axis of the third section (shaft 1) of the mechanism 3 also depends on the number of sections and is inversely proportional. Given two strands of flexible connection, the force T _A is determined by the formula:

$$T_A=\frac{2T_{\mathrm{one}}}{k}$$

The tension forces of the flexible bond threads T ₁ and T ₂ (FIG. 3) are determined by the following formulas:

$$T_{\mathrm{one}}=\frac{P}{Sin\alpha Cos\beta +Sin\beta Cos\alpha }$$

$${\mathrm{<figure-callout\; id="2"\; label="T"\; filenames="00000016.png"\; state="\{\{state\}\}">T</figure-callout>}}_2=\frac{P(Cos\alpha -Sin\alpha tg\beta )}{Sin\alpha +Cos\alpha tg\beta }$$

where P is the force acting on the flexible communication thread at the moment of collision with the pulsator 8, determined by the formula P = M _KP / d, where d is the arm of the pulsator 8 (Fig.3).

Then

$$T_{\mathrm{one}}=\frac{M_{KP}}{d(Sin\alpha Cos\beta +Sin\beta Cos\alpha )}$$

$${\mathrm{<figure-callout\; id="2"\; label="T"\; filenames="00000016.png"\; state="\{\{state\}\}">T</figure-callout>}}_2=\frac{M_{KP}(Cos\alpha -Sin\alpha tg\beta )}{d(Sin\alpha +Cos\alpha tg\beta )}$$

Therefore, the force T _A transmitted by the parallelogram mechanism 3 to the rotating shaft 1 in the collision of the flexible communication threads with the pulsator should be determined by the formula:

. $$T_A=\frac{2M_{KP}}{kd(Sin\alpha Cos\beta +Sin\beta Cos\alpha )}$$

.

The action of the flexible coupling 6 on the roller 13 in a collision with the pulsator 8 causes a reaction of the support T _B (Fig. 3), which depends on the tension force of the flexible coupling T ₁ , the angle α ° defining the direction of the thread, and also on the external resistance force R _C , preventing the free movement of the installation in space.

Force T _{B is} defined as the vector sum of these quantities by the formula:

. $${\overline{T}}_B={\overline{T}}_{\mathrm{one}}+{\overline{R}}_{\mathrm{FROM}}$$

.

The resistance force R _C is determined by known methods depending on the purpose of the installation and the scope of its application on the vehicle. When starting off on the surface, the static friction force should be determined using a static coefficient of friction. When moving in a continuous air or water environment, it is necessary to determine the strength of the aerodynamic or hydrodynamic drag, since in this case the drag force depends on the speed of the device.

The dynamic equilibrium of all active forces acting on the claimed installation relative to the coordinate axis X, which coincides with the direction of movement of the housing 14, is determined by the d'Alembert principle and is achieved provided:

$$F_{\mathrm{and}}=2(T_{\mathrm{one}}-T_{2}Cos\alpha )+R_C$$

T _A = R _C

Since the inertia force F _and = m ₁ ω ² R = 2 (T ₁ -T ₂ Cosα) + R _C , the threshold value of the angular velocity of rotation of the shaft 1 is expressed by the formula

$$$$

$${\omega }_P=\sqrt{\frac{2(T_{\mathrm{one}}-T_{2}Cos\alpha )+R_C}{m_{\mathrm{one}}R}}$$

threshold speed -

$$n_P=\frac{\mathrm{thirty}{\omega }_P}{\pi }=9.5\frac{2(T_{\mathrm{one}}-T_{2}Cos\alpha )+R_C}{m_{\mathrm{one}}R}$$

where R is the distance from the axis of the rotating shaft 1 to the axis 5 of the load 4 (figure 3).

With an increase in the angular velocity (ω _p ) of the shaft 1, with the lever 2, the mechanism 3 and the load 4, the condition of dynamic equilibrium will be violated and the housing 14 will change its position, since it will receive translational motion from the shaft 1.

With a further increase in the speed of rotation of the shaft 1, a change occurs in the ratios of the forces acting on the housing 14 and the installation leaves the state of dynamic equilibrium:

F _and ≥2 (T ₁ -T ₂ Cosα) + R _C

T _A > R _C.

Vector traction device F _T coincides with the direction of action of force T _A and inertial forces F _u and is given by:

F _T = T _A + F _and + 2T ₂ Cosα-2T _B Cosγ,

where γ is the angle of deviation of the vector T _B from the coordinate axis X.

The traction force of the installation, with the corresponding power of the shaft 1, can reach significant values. If the traction force exceeds the resistance to movement of the installation casing (F _T > R _C ), then a driving force F is created, which drives the device in translational motion:

F = F _T -R _C.

When determining the dynamic characteristics of the claimed installation, it should be borne in mind that the driving force acts on the installation impulsively, depending on the frequency of rotation of the shaft 1.

The intensity of the driving force (k) is determined by the number of collisions of the flexible connection 6 with the pulsator 8 per unit time:

$$k=\frac{n}{60}(c^{-\mathrm{one}})$$

The duration of the pulse depends on the angle of rotation of the lever 2 (α) (figure 3) and frequency of rotation:

$$\tau =\frac{\alpha }{6n}(c)$$

Then the elementary momentum of the driving force will be:

ΔS = F · τ,

which, with uniform rotation of the lever 2 (ω = const, ε = 0), is a constant value. Therefore, the total momentum over a certain period of time t is defined as the product of the elementary momentum ΔS and the number of collisions of a flexible connection with a pulsator:

∑S = ΔSkt.

Using a flexible coupling, the momentum ΔS is transmitted instantaneously to the installation casing with a duration of τ = 0.0201 ÷ 0.0015 s at a shaft revolution of 1 n = 230 ÷ 3000 rpm. During this time, the lever 2 with the load 4 and the mechanism 3 moves along the relative trajectory of all by an angle α = 0.1 ° ÷ 28 °, which makes the installation progress smoother and quieter.

The speed of the installation is determined according to the theorem on the change in the amount of movement according to:

M (VV _O ) = ∑S,

where M is the mass of the device

V - initial speed

V - final speed

∑S is the total momentum.

The required power of the claimed installation is determined at the maximum angular velocity of the lever 2 (ω _MAX ) and the corresponding value of the peripheral force (P _MAX ); acting on the pulsator 8:

N = P _MAX dω _MAX .

When using the installation on vehicles or other objects with energy sources for shaft rotation, the parameters of traction, speed, required power, etc. are determined taking into account the total mass of the object with the payload and operating conditions.

Figure 4 presents the current installation model on an open moving platform.

Figure 5 presents the current model of the vehicle with the installation that converts the kinetic energy of the rotating shaft into accelerated translational motion, on three smooth supports.

Information sources

1. RU 2408808 C1, IPC F16H 19/00.

2. RU 2416048 C2, IPC F16H 19/00.

3. RU 2411139 C1, IPC V60G 5/00.

List of designations adopted in the application

1. The shaft of rotation.

2. Lever.

3. The acceleration mechanism.

4. Cargo.

5. The axis of the cargo.

6. Flexible connection.

7. Slider.

8. The pulsator.

9. Bracket with slots.

10. Connecting bracket.

11. The axis of the first section of the mechanism 3.

12. Bracket.

13. Roller.

14. The housing.

15. The protrusion of the bracket 10.

Claims (1)

Installation for moving in space, converting the kinetic energy of a rotating shaft into accelerated translational motion of the housing on the surface, comprising a housing, a rotating shaft mounted therein with a movable arm perpendicular to the load and the acceleration mechanism, two pulsators, flexible connection, characterized in that the installation additionally contains a speed-up mechanism that converts the force of the flexible connection into the traction force of the installation, with parallelogram sections pivotally interconnected, sewing along smooth lever rods, and pivotally mounted at one end on the rotation shaft, the other on the load axis, flexible connection with two parallel threads of finite length, fixed at one end on the rotating lever, and the other on the axis of the section of the acceleration mechanism, while covering pulsators and load rollers whose axes are parallel.

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