RU2034170C1 - Inertial centrifugal engine - Google Patents

Abstract

FIELD: power engineering. SUBSTANCE: principle of operation of the engine is based on interaction of pairs of unbalance weights which rotate with respect to each other in the opposite directions and in the perpendicular planes. This combined rotation results in movement of the unbalance weights over curved trajectories of hemispheres of spherical surfaces, the weights being positioned constantly in the region of 0- 180 deg. The resultant force rotating the unbalance weights always points to the one direction. EFFECT: enhanced efficiency. 5 dwg

Description

 The invention relates to mechanical engineering, and more specifically to the automobile and aircraft industries and can be used as a traction power plant and reverse brake on cars, aircraft, individual vehicles driven by muscular power, as well as when creating a universal type of transport inertial Suspension moving on the ground and in the air.

 An inertial motor is known, in which disordered centrifugal inertia forces are converted into a linear force, the energy of which causes a directed movement, consisting of four systems, each system has one unbalanced load and one planetary gear common to all drive systems.

 However, in the indicated inertial motor, pulses of the resulting force of centrifugal inertia forces (hereinafter referred to as CSI) of unbalanced loads acting alternately in one direction, as well as second-order inertia forces of inertia moments of masses of unbalanced loads arising from their rotation in planes perpendicular to the axis of rotation of the systems, will cause vibration loads on the inertial motor and transfer them to the vehicle on which the inertial engine is installed. In addition, in the kinematic diagram of an inertial motor, the diameters of planetary gears cannot be less than two radii of rotation of unbalanced weights (more precisely, the length of the frames of the systems), in this case, gears of large diameters and additional large masses such as flywheels are required to balance each gear of a planetary gear, increase the strength and an increase in the size of other parts, which makes the construction of the inertial motor cumbersome and significantly reduces the effectiveness of its application.

 The aim of the invention is to create a compact, efficient and simple inertial motor design with developed sliding bearings of unbalanced loads and frames that can withstand heavy loads of the center of rotation during the rotation of unbalanced weights, to differentiate their resulting center of reference of constant magnitude and unidirectional action, as well as eliminate external manifestations of vibration loads.

This goal is achieved by the fact that each system of an inertial motor uses unbalanced loads of an axial-free design of a segment type, which are installed in pairs in conjunction with their planetary gears, are supported by their outer cylindrical sliding surfaces on the inner cylindrical sliding surfaces of the frame and form systems, planes of rotation of unbalanced goods two systems are rotated relative to the other two systems at an angle of ^about 90, the resultant forces pulses SRC steam systems with are shifted in phase and differentiated into a constant force, causing unidirectional motion of the inertial motor, and the resulting second-order inertia forces of the moments of inertia of rotation of unbalanced weights are equalized by the amplitude of the oscillations. The complete elimination of the manifestation of the second-order inertia force is achieved by the successive installation of four pairs of systems rotated by one pair relative to another by an angle of 45 ^° .

 In FIG. Figure 1 shows an inertial motor consisting of body 1, two right-handed systems A1, A3 and two left-handed systems A2, A4, a rotation mechanism of systems B. Each system consists of a frame 2, two unbalanced weights 3, a planetary gear C for rotating unbalanced weights 3.

 The housing 1 is a rectangular box-shaped, in which four through holes and four blind holes are drilled, which are supporting bearings for the frames 2 of the system, from the side of the through holes the cover 10 of the housing 1 with the drive gear 9 is attached.

 Frame 2 is made in the form of a rotor with external sliding bearings and a perpendicular intersecting cylinder, inside of which on the sliding bearings there are unbalanced loads with planetary gears, fixed from axial displacement by retaining rings, holes are made along the frame axis at the ends of the gear axis 5 of planetary gear C and the gear system drive 6.

 The unbalanced load 3 is a sector of the circle, made slightly larger than the semicircle, axisless type, the sliding support is the outer cylindrical surface of the semicircle, which it rests on the inner cylindrical sliding surface of the frame 2, along the axis of rotation there is a hole for installing the gear 4 of the planetary gear. The area of the sliding bearings of one unbalanced load 3 and the frame 2 of this load on the proposed inertial motor according to calculations can withstand the working load of the center for more than 1200 kg (when using materials used in mechanical engineering in its design).

Planetary gearing C consists of two bevel gears 4 installed in the axial openings of unbalanced weights 3 and a bevel gear 5, which is tightly fixed with its end in the hole of the housing 1. (In systems A1 and A3, to ensure clockwise rotation of these systems, gears 5 are deployed on 180 ^about in relation to the same gears of systems A2 and A4, and the axes of the first are elongated).

 The rotation mechanism of systems B consists of gears of the drive of systems 6, made integral with the frames 2, an intermediate gear 7 located on the axis 8 and fixed in the cover 10 of the housing 1 of the gear of the drive 9.

 The drive of the device is carried out from the engine (or muscular force through the gearbox) through the clutch 11.

 The device operates as follows.

In the initial position, the unbalanced loads 3 of systems A1 and A2 are directed in opposite directions parallel to the axes of the frames 2, which corresponds to the position of the centers of mass of the unbalanced loads 3 at points 0 and 180 ^{about the} angle of rotation of the systems, the momentum of the resulting force of the center of rotation of their unbalanced loads 3 is 0; unbalanced loads of 3 systems A3 and A4 are shifted in phase angle of rotation relative to systems A1 and A2 by 90 ^° , their radii are perpendicular to the plane of the housing 1, and the impulse of the resulting force of the center of motion is maximum. The decrease in the impulse of the resulting force of the center of the unbalanced cargo 3 systems A3 and A4 is compensated by the increment of the pulse of the equal force of the center of the unbalanced cargo 3 systems A1 and A2. Thus, a shift of the angle of rotation of systems A3 and A4 relative to systems A1 and A2 by 90 ^° provides a differentiation of the resulting forces of the center of rotation of unbalanced weights 3 of systems A1, A2, A3, A4 due to the continuous, constant in magnitude and unidirectional action (see Fig. 5).

The rotation of the systems is transmitted from the drive motor through the coupling 11. When the system rotates, the bevel gears 4 roll around the gear 5 and rotate the unbalanced weights 3 in planes parallel to the longitudinal axis of the frame 2, as a result, the unbalanced weights 3 rotate in opposite directions and simultaneously in two perpendicular planes: 2 and relative to the frame together with the frame 2 relative to the housing 1, the centers of mass unbalance goods 3 are moved along curvilinear trajectories of ball surfaces in the region ^of 0-180 at an angular velocity in two pa and greater angular speed frame, an impulse of the resultant force of rotation of unbalanced loads CSR systems 3 is always directed perpendicular to the axes of rotation of said side frames in the hemispheres. During the rotation angle of the frame 2 180 unbalance loads ^about 3 turn through an angle of 360 ^° (see. Fig. 3).

Rotating A1 system clockwise (see. Fig. 2, I, II) A2 system is rotated counterclockwise, the angle of rotation of unbalanced loads 3 grows and reaching angle ^90, centers of the radii of their masses will assume a position perpendicular to the plane of the housing 1, and the impulse of the resulting force of the unbalanced loads of systems A1 and A2 will also be directed perpendicular to the plane of the housing 1 and applied to its center, at the same time, the systems A3 and A4 rotate identically with respect to the systems A1 and A2, their unbalanced loads 3 will reach an angle of rotation of 180 ^° and will be directed in contrast s hand, the unbalance loads 3 will return to ^about 0-180 zone, i.e. to the starting position. The radii of rotation of the unbalanced mass center 3 when the goods in their position, angle of rotation ⁹⁰ and rotated in a plane perpendicular to the longitudinal axis of the frame 2, is longer than the actual radii of unbalanced loads 3 constitute value r RSin φ˙ctgα due to the asymmetry of the location of unbalance loads about axes 3 rotation of the frames 2, and decrease to the size of the asymmetry at rotation angles of 0 and 180 ^about (see Fig. 3). At points 0 and 180 ^{about the} mass of unbalanced weights 3 of each system create moments of forces tending to rotate the system around an axis perpendicular to the axis of the frame 2. The moments of these forces are balanced by the relative position of the unbalanced weights 3 of the systems.

According to the principle of independence of the action of forces during the rotation of unbalanced loads of 3 systems in two perpendicular planes, the following forces arise:
P _{1 the} resulting force of the center of rotation of unbalanced loads 3 in planes passing parallel to the axis of rotation of the frames 2 of systems A1 and A2;
P _{2 the} resulting force of the center of rotation of unbalanced weights 3 in planes extending perpendicular to the axes of the frames 2 of systems A1 and A2;
P _{3 the} resulting force of the center of rotation of unbalanced loads 3 systems A3 and A4, equal to P ₁ ;
P _{4 the} resulting force of the center of rotation of unbalanced loads 3 systems A3 and A4, equal to P ₂ ;
P is the resultant CSI force equal to the sum of the force vectors P ₁ , P ₂ , P ₃ , P ₄ ;
T is the resulting inertia force of the second order arising from the rotation of unbalanced weights 3 with a variable radius r in a plane perpendicular to the axis of rotation of the frames 2, and the change of orbits by the centers of mass of unbalanced weights 3.

 In the diagram of FIG. 2 and 3 show the positions of unbalanced weights 3 relative to the frames 2 and frames 2 relative to the plane of the housing 1 during rotation of the systems, as well as the inertia forces arising in the systems and their resulting.

The value of the inertia force (see Fig. 2) P ₁ 4mR ω ² Sin ² φ where m is the mass of one unbalanced load 3, in kg (the mass of all unbalanced loads 3 is the same);
R is the radius center of mass of unbalanced weights 3, in m, (radius of rotation "const");
ω the angular velocity of the unbalanced cargo 3 relative to its own axis of rotation, in rad / sec;
φ the angle of rotation of the unbalanced cargo 3 relative to the plane of the frame 2, equal to the angle of rotation of the frame 2 relative to the plane of the housing 1;
Sin ² φ is the product of the sines of the angles of rotation of the unbalanced weights 3 relative to the plane of the frame 2 and frame 2 relative to the plane of the housing 1.

The value of the inertia force (Fig. 2 and 3) P ₂ 4mr ω ² 2Sin φ 4mR ω ² 2Sin ² φ since r RSin φ ^. ctg α ^. cos β where m is the mass of unbalanced load 3, in kg;
r radius of rotation of unbalanced weights 3 perpendicular to the axis of the frame (variable value, varies from 0 to R), in m;
β angle of inclination of radius r to the plane of rotation of unbalanced loads;
ω angular velocity of unbalanced loads 3 in rad / s;
φ the angle of rotation of the unbalanced cargo 3 relative to the plane of the frame 2, equal to the angle of rotation of the frame 2 relative to the plane of the housing 1, φ '.

The formula shows that the forces P ₁ and P ₂ are equal in magnitude.

· tgφ/ где I

где I момент инерции дебалансных грузов 3 при смене ими орбит вращения вокруг осей рамок 2, кг˙м/кв;
ω угловая скорость дебалансных грузов 3 в рад/с;
tg φ период изменения I;
φ угол между радиусом вращения дебалансного груза 3 и вектором равнодействующей касательной и нормальной сил момента инерции I этого груза.The value of the inertia force (see Fig. 3)
T

Tgφ / where I

where I is the moment of inertia of unbalanced loads 3 when they change rotation orbits around the axes of frames 2, kg˙m / sq;
ω angular velocity of unbalanced loads 3 in rad / s;
tg φ period of change I;
φ is the angle between the radius of rotation of the unbalanced load 3 and the vector of the resultant tangent and normal forces of the moment of inertia I of this load.

The inertia force of the second order T changes every 90 ^{about the} angle of rotation of the unbalanced weights 3, this force is directed in the opposite direction of the force P and is 1-2% of the center of rotation of the unbalanced weights 3.

 The calculated values of the center of rotation of unbalanced weights 3 with masses m 0.1 kg and a radius of their rotation R 0.02 m, 4000 rpm of systems in the described inertial motor are summarized in the table (see Fig. 4) and shown in the graph (see Fig. . 5), approximate overall dimensions of the inertial motor 160x160x120 mm.

Claims (1)

An inertial centrifugal engine containing a casing that is multiple to two rotating in opposite directions in the perpendicular planes of the system, interconnected via a planetary gear, the output shaft of which is connected to the drive, each of the rotating systems consists of rectangular frames, pins mounted on the casing, unbalanced frames are installed weights, on shafts associated with the transmission, unbalanced weights are mounted for rotation in opposite directions with the centers of mass moving along the curves a linear trajectory, characterized in that in each rotating system the frame is made in the form of a rotor mounted in a housing on sliding bearings with a cylinder perpendicular to it intersecting inside, inside of which on the sliding bearings there are unbalanced loads with a planetary gear rotating in the cylinder and made in the shape of a sector circles installed in the cylinder in parallel, their rotation planes are offset relative to the longitudinal axis of the frame, while the planes of rotation of unbalanced loads of rotating pairs of systems are rotated one tnositelno another 90 ^o, and the centers of mass of unbalanced loads one pair systems are alternately directed in opposite directions and another pair systems are alternately directed towards the unidirectional movement.

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