JP2023121171A - Thrust generation device using synthetic vibration wave - Google Patents

Abstract

To make vibration periods of sine waves of a vibration plate and half-sine pulse wave of a recoil plate coincident with each other to generate inertial force with synthetic vibration, without requiring a reaction force due to jets such as fossil fuels to the outside of a device, on the ground and in space.SOLUTION: A plurality of vibration devices that generates unbalanced centrifugal force by a weight 3 is arranged evenly on a disc diaphragm 5, and their positions are synchronously controlled by a system motor 1; the diaphragm 5 and a vertical shaft 4 are fixed; the vertical shaft 4 is made to stand upright without being connected to the center of a disc reaction plate 10 whose outer periphery is fixed; the diaphragm 5 and the reaction plate 10, which are made of flexible metal materials, are equally interlocked by the rotational stress of the weight 3; a length from an upper end of an adjustment nut 11 to a lower end 4a of the vertical axis is set to a fixed reference length; and by controlling the vibration range of the reaction plate 10, thrust due to inertial force can be generated by a composite wave of a half-sine pulse wave due to the restoring force of the reaction plate 10, which has the same vibration period as the sine wave of the diaphragm 5.SELECTED DRAWING: Figure 1

Description

The present invention relates to a propulsive force generating device that obtains propulsive force from the inertial force of synthetic wave vibration generated by a diaphragm and a reaction plate without emitting a jet to the outside, unlike a rocket engine or the like.

Earth gravity escape velocity is required to reach outer space from the ground and operate, and a large amount of launch fuel is required to propel the rocket to obtain acceleration. In addition, jet engines of airplanes emit a large amount of high-temperature gas and cause global warming. In addition, these aircraft are affected by weather conditions, and depending on the situation, they cannot fly, and flight cancellations occur frequently.

As a measure to improve this, a propulsive force generating device using synthetic vibration waves is provided that does not require a reaction by a jet on the outside of the device, and inertial force acts only in a specific direction, and is extremely safe.

Japanese Unexamined Patent Application Publication No. 2001-73927 Japanese Patent Application No. 2008-522224

Vibrations are tangible waves and affect all objects. For example, it is possible to synthesize an A-oscillating wave that travels in a medium and a B-oscillating wave that travels in the opposite direction. It has also been proved that the combined vibration of two waves propagates through a medium as wave independence.

There is a wave called a shock pulse, and in a dynamic system, it is a wave that gives an excessive dynamic disturbance to an object. This has been applied as a wave effect during shock testing of electronic products such as those used in electronics, automobiles, the aerospace industry, and the like.
Among several types of shock pulses, a half-sine pulse wave refers to a half-cycle waveform of a half-sine wave, that is, only a positive portion or a negative portion.
SUMMARY OF THE INVENTION An object of the present invention is to amplify vibration energy in a specific direction by synthesizing a half-sine pulse wave with a sine wave to obtain a driving force by inertial force.

In order to form the composite wave, the object is to generate a sinusoidal half-pulse wave by applying the vibration of the sinusoidal wave generated in the diaphragm and the restoring force of the reaction plate, and to combine them efficiently.

The invention for solving the above problems is a vibrating device that generates an unbalanced centrifugal force and is composed of a rotor 2 and a bearing 6 to which a weight 3 and an arm 16 are attached, and a plurality of vibrating devices that are discs. The diaphragm 5 is evenly arranged at the end of the diaphragm 5, and the system motor 1 connecting the vibration device with the joint 7 controls the synchronous position, and the center of the diaphragm 5 is connected to the vertical shaft 4 having the central axis 19 as the axis, and the disk or a support frame 15 is fixed to the reaction plate 10, an adjusting ring 11 is attached to the vertical shaft 4, and the vertical shaft 4 is supported by the slide bearing 12 and the horizontal frame 9. The length from the upper end of the adjustment wheel 11 to the lower end 4a of the vertical shaft is the length from the impact receiver 9a of the horizontal frame 9 that intersects the central axis 19 to the equilibrium line 10a (upper surface of the recoil plate) that also intersects the central axis 19. Matching the fixed reference length 20, the vertical axis 4 is erected without being coupled to the center of the reaction plate 10. - 特許庁

The vibration plate 5 and the reaction plate 10 are made of a flexible metal material, mainly a ferrous metal material. Both sizes and thicknesses are determined so that the amounts are equal or the amount of bending of the reaction plate 10 is small. According to Hooke's law, the amount of deflection due to stress and the amplitude of vibration are in the same relationship.

When the weight 3 of the vibration device is synchronized in rotation with the system motor 1, the vibration plate 5 vibrates sinusoidally due to the centrifugal force, and the reaction plate 10 in contact with the vertical shaft 4 also vibrates due to the force, and the amount of deflection of both is equal. In this case, the vibration plate 5 and the recoil plate 10 vibrate with the same amplitude and period, and the vertical shaft 4 and the recoil plate 10 vibrate in close contact with each other.

When the adjustment wheel 11 attached to the vertical shaft 4 impacts the impact receiver 9a at the lower end of the horizontal frame 9, the reaction plate 10 and the lower end 4a of the vertical shaft momentarily stop at the equilibrium line 10a, and cannot physically vibrate upward. The impact vibration due to the restoring force of the reaction plate 10, which has the same amplitude and period as the diaphragm 5, propagates along the vertical axis 4 as a sine half-pulse wave that is half the wavelength of the sine wave, and the sine wave of the diaphragm 5 and the vibration period will form a composite wave with equal

Since the present invention is configured as described above, it has the following effects.

The metal materials used for the vibration plate 5 and the reaction plate 10 may be a combination of metal materials having somewhat different elastic moduli such as Young's modulus and tensile strength as long as they vibrate sinusoidally. are equal to each other, or when the amount of deflection of the reaction plate 10 is small, the two vibration periods match each other.

As a configuration for generating a sine half-pulse wave, the length from the upper end of the adjustment wheel 11 attached to the vertical shaft 4 to the lower end 4a of the vertical shaft 4 is extended from the impact receiver 9a at the lower end of the horizontal frame 9 that intersects with the central axis 19 to the same central axis. By matching the fixed reference length 20, which is the length to the equilibrium line 10a (upper surface of the recoil plate) of the recoil plate 10 that intersects with 19, the vibration range of the recoil plate 10 is physically limited by the vertical axis 4, and the recoil plate 10 vibrates only downward from the equilibrium line 10a and cannot vibrate upward.

Since the vertical shaft 4 and the recoil plate 10 are not coupled, even if the vibrating plate 5 vibrates upward from the equilibrium state due to the centrifugal force of the weight 3, the recoil plate 10 is not affected by the centrifugal force, and the equilibrium line 10a In the lower range, the vertical shaft 4 and the reaction plate 10 vibrate while being in close contact with each other.

Therefore, when the adjustment wheel 11 attached to the vertical shaft 4 impacts the impact receiver 9a due to the restoring force of the reaction plate 10, the impact force becomes a half-sine pulse wave corresponding to the half wavelength of the sine wave, propagates through the vertical shaft 4, and vibrates. It combines with the sine wave of the plate 5 to generate an inertial force.

If the amplitude of the recoil plate 10 is smaller than that of the diaphragm 5, even if the wavelength of the recoil plate 10 is shortened, the oscillation period of the recoil plate 5 is not delayed, so the vertical shaft 4 and the recoil plate 10 vibrate in close contact with each other. Generate inertial force.

However, when the amplitude of the recoil plate 10 becomes larger than that of the diaphragm 5, the vibration cycle becomes longer and lags behind, so that the vibrations do not coincide with each other. Therefore, the vibration plate 5 and the reaction plate 10 are made of metal materials having the same characteristics such as elastic modulus.

1 is a front view 1 showing an embodiment according to the present invention; FIG. FIG. 2 is a front view 2 showing an embodiment according to the present invention; FIG. 4 is an explanatory diagram of a composite wave composed of a sine wave and a sine half-pulse wave; It is a perspective view of an experimental device. FIG. 10 is a diagram showing how the recoil plate is fixed by the hollow fixing ring; It is a figure which shows the synthetic|combination point of a sine wave and a sine half-pulse wave.

Examples will be described below in detail based on experimental results.

Experimental example 1
FIG. 4 shows an experimental apparatus according to the present invention. SPCC (cold-rolled mild steel plate), which is an iron-based metal material, was used for the vibration plate 5 and the reaction plate 10, both of which are discs. In the case of the vibration plate 5, the deflection calculation formula of the metal material is a central concentrated load with the center of the disc fixed to the vertical shaft 4, Equation 1. Central concentrated load fixed around several points by 21. In Equation 2, the stress concentrates on the center of the disc.

In the experimental apparatus, in order to synchronize the rotation of the weight 3 of the arm 16 attached to the rotor 2, the small bevel gear 18 attached to the motor 13 is meshed with the large bevel gear 17 having the vertical axis 4 as the rotation axis, and the joint 7 is set. Rotate the bearing 6 via. Three of these vibrating devices are evenly arranged on a disk diaphragm 5, the center of the diaphragm 5 is connected to the vertical shaft 4, a support frame 15 is fixed to a disk reaction plate 10, and an adjustment wheel 11 is attached. The attached vertical shaft 4 is supported by the slide bearing 12 and the horizontal frame 9, and is erected without being connected to the center of the reaction plate 10. - 特許庁

The total mass of the arm 16 (made of aluminum) and the weight 3 (iron plate) is 15.3g. Rotor 2 material SPCC, diameter 12 cm, thickness 2.3 mm. The motor 13 is a DC motor with a 12V current control system, and is connected to an external controller. The vertical shaft 4 has a diameter of 10 mm (made of stainless steel), and the total centrifugal force of the weight 3 generated by these three motors is assumed to be 200N.

In order to install the motor 13 and the vibration device consisting of three rotors 2 and bearings 6, the diaphragm 5 has a diameter of 400 mm and a thickness of 2.0 mm, and the reaction plate 10 has a diameter of 300 mm and a thickness of 1.2 mm. did. If the diameter of the recoil plate 10 is set to 296 mm, theoretically, both deflection amounts can be matched, and if a stress of 200 N is applied, the deflection amount relative to the central axis 19 will match at 2.75 mm. . Also, the amount of deflection is always the same, which is 5.51 mm with a stress of 400 N and 11.03 mm with a stress of 800 N.

The Young's modulus (modulus of longitudinal elasticity) of metal materials has the following relationship.
Young's modulus (E) = stress (σ) / strain (ε)
The vibration plate 5 and the reaction plate 10 have the same elastic modulus such as Young's modulus because they are made of the same metal material. Moreover, since the stress due to the centrifugal force acting on both is interlocked by the vertical axis 4, it is equal. Therefore, in the case of the reaction plate 10 having the same shape as the diaphragm 5 but different only in the fixing method, if the thickness and size of the plate are appropriate, the amount of relative deflection with respect to the central axis 19 becomes the same as the stress changes, and the diaphragm 5 and the reaction plate 10 vibrate in a relationship that the vibration amplitude and vibration period are always equal.

The vibration acceleration of the vibration plate 5 at the time of natural vibration is 10.1 m/ ^sec2 , which is somewhat larger than the gravitational acceleration. too much and was unsuitable as an experimental material.

The no-load rotation speed of the motor 13 used in the experiment is 8170 rpm (136 Hz), and the natural frequency of the diaphragm 5 is 30.2 Hz when calculated from the spring constant. Since the diaphragm 5 is connected to the vertical shaft 4 at its center, there is damping, and the external force from the motor 13 acts at a speed faster than the natural vibration, resulting in a phase lag.

The experimental device was installed on an electronic scale, and the outer circumference of the reaction plate 10 was fixed to the top plate of the electronic scale at several points with fixing metal fittings 21, and the propulsive force generated in the experimental device was observed.

Since the members of the experimental apparatus have been partially improved, the principle of the invention will now be described with reference to FIGS. 1 and 2 showing an embodiment of the present invention.
A vibrating device comprising a rotor 2 and bearings 6, a vibrating plate 5, and a reaction plate 10 are the same as those of the experimental device. The bearing of the slide bearing 12 of the experimental device was modified to a slide unit suitable for vertical movement in this example.

In addition, the disk reaction plate 10 is fixed by a base ring 23 and a hollow fixing ring 22 having the same outer diameter, the support frame 15 is fixed to the hollow fixing ring 22 or the reaction plate 10, and the vertical shaft 4 is connected to the plain bearing 12 and the horizontal shaft. The vertical shaft 4 supported by the frame 9 and fitted with the adjustment wheel 11 is erected without being connected to the center of the reaction plate 10. - 特許庁

If the length of the fixed reference length 20, which is the length from the impact receiver 9a of the horizontal frame 9 intersecting the central axis 19 to the equilibrium line 10a (upper surface of the reaction plate) also intersecting the central axis 19, is, for example, 200 mm, the reaction The distance from the lower end 4a of the vertical shaft contacting the plate 10 to the upper end of the adjusting wheel 11 is adjusted to 200 mm and fixed. Furthermore, if the diaphragm 5 with the vibrating device or the like mounted on the upper side of the vertical shaft 4 is installed with the fixing nut 8, even if the load between the adjustment wheel 11 and the impact receiver 9a is bent, the adjustment is not performed. Even if the reaction plate 10 is flexed under the influence of gravity, a faster vibration acceleration (restoring force) is generated in the reaction plate 10 to cancel the flexure.

Four system motors 1 are evenly arranged on the diaphragm 5, and a hollow fixing ring 22 of the device is fixed to the outside with a fixing screw 24. As shown in FIG.

When the apparatus of this embodiment having the above structure is started, the centrifugal force of the weight 3 causes the vibration plate 5 to bend and vibrate sinusoidally, and at the same time, the reaction plate 10 in close contact with the vertical shaft 4 also vibrates. do. The restoring force of the reaction plate 10 causes the vertical shaft 4 to vibrate from the troughs to the peaks of the vibration waveform. The shaft lower end 4a stops momentarily at the equilibrium line 10a.

Therefore, the reaction plate 10 does not flex and vibrate upward, and when the weight 3 of the rotor 2 rotates by 180°, the vertical shaft 4 begins to descend again and the reaction plate 10 bends downward. Become.

Further, when the vibration acceleration is amplified beyond the gravitational acceleration and the recoil plate 10 receives vibration from the vertical shaft 4 , the vibration energy due to the centrifugal force of the weight 3 is accumulated in the recoil plate 10 . Since the vibration plate 5 and the reaction plate 10 have the same amount of deflection and the same frequency, they also have the same vibration amplitude and vibration speed.

Therefore, the recoil plate 10 and the vertical shaft 4 vibrate in close contact with each other, and when the adjustment wheel 11 attached to the vertical shaft 4 impacts the impact receiver 9a at the lower end of the horizontal frame 9 due to the restoring force of the recoil plate 10, the impact vibration is vertical. It propagates along the shaft 4 and reaches the diaphragm 5 .

The impact vibration of the reaction plate 10 is a half-amplitude that does not vibrate upward, and has only a positive component that is a force in the upward direction. You can call it a wave.

Since this sine half-pulse wave coincides with the vibration period of the sine wave of the diaphragm 5, both vibration waves become a composite vibration wave on the diaphragm 5, and a propulsive force is generated upward due to the inertial force.

FIGS. 3(a), 3(b) and 3(c) show a series of formation processes of the composite wave.
(a) shows the situation where the sine wave of the diaphragm 5 travels from the bearing 6 side to the vertical axis 4 .
(b) shows a situation in which the restoring force of the reaction plate 10 impacts the adjusting screw 11 against the impact receiver 9a, and the sine half-pulse wave propagates along the vertical shaft 4 and advances toward the bearing 6 side.
(c) shows the direction in which the inertial force is generated by synthesizing both vibration waves.

FIG. 5 shows how the recoil plate 10 is fixed by the hollow fixing ring 22 .
(a) is a perspective view of a hollow fixing ring 22. FIG.
(b) is a cross-sectional view of the above.

FIGS. 6(a) and 6(b) are diagrams showing the leading synthetic point where the sine wave and the sine half-pulse wave overlap. Synthesis occurs only between straight lines of the bearing 6 and the vertical axis 4 where the force acts, where the vibration periods coincide.
(a) shows the case where three vibration devices such as bearings 6 are installed.
(b) shows the case where four of the above devices are installed.

The propulsive force observed in the experimental apparatus is such that the mass of the apparatus is constantly reduced by about 1.5 to 2 kg, and the rotation speed of the weight at this time is about 1900 to 2000 rpm.

Since the diaphragm 5 rotates due to the rotational couple of the weight 3, it is stabilized by providing a detent for restraining the end of the diaphragm 5 and the like.

Experimental example 2
The vibrating device consisting of the rotor 2 and the bearing 6 and the diaphragm 5 were the same devices from Experimental Example 1 to Experimental Example 4, and the experiments were conducted by replacing only the reaction plate 10 . When the diameter of the reaction plate 10 is 300 mm, which is the same as in Experimental Example 1, and the SPCC metal material is 1.0 mm thick, the amount of static deflection is 4.88 mm, which is larger than the amount of deflection of the diaphragm 5 of 2.75 mm. When this is vibrated, the amplitude of the reaction plate 10 is large, so that the vibration mode is different from that of the sine wave, and the reaction plate 10 and the vertical shaft 4 vibrate apart, and they impact each other, causing disturbance vibration. The recoil plate 10 having a greater amount of deflection than the vibration plate 5 has a different period.

Experimental example 3
If the reaction plate 10 is made of SPCC metal material with a diameter of 300 mm and a thickness of 1.6 mm, a propulsive force is generated even if the amount of deflection is 1.19 mm. This is because both are made of the same metal material and have the same elasticity, so that the reaction plate 10 vibrates in close contact with the vertical shaft 4, generating a sine half-pulse wave with a short wavelength in proportion to the amplitude. Since this sine half-pulse wave and the sine wave of the diaphragm 5 have the same period even though the amplitude is different, they are synthesized in a one-to-one relationship. Since the restoring force is also affected by the mass of the reaction plate 10, a propulsive force equivalent to Experimental Example 1 was observed, although unstable. Theoretically, if the diameter of the recoil plate 10 is set to 454 mm, the amount of deflection will be 2.73 mm, which is the same as that of the diaphragm 5, and the mass will increase, so the restoring force will also increase.

Experimental example 4
An experiment was conducted using a stainless plate (SUS304) with a diameter of 300 mm and a thickness of 1.5 mm as the recoil plate 10 . The amount of static deflection is 1.45 mm, and the tensile strength of the SPCC material is 270 Mpa, while the stainless steel plate is 520 Mpa, which is about twice the tensile strength. At the beginning of the oscillation, there are signs of propulsive force, but it soon becomes unobservable. It is difficult to match the dynamic deflection rates of materials with large differences in tensile strength. However, since it does not exceed the elastic limit, if the diameter is 414 mm, the amount of deflection will be 2.77 mm and the amplitude will be the same.

From the above experimental results, the materials used for the vibration plate 5 and the reaction plate 10 may be a combination of metal materials having somewhat different Young's modulus and elastic modulus of tensile strength. can be said to occur.

1 and 2 as an embodiment, the system motor 1 for cycle-synchronous position control of the weight 3 incorporates a motor, an encoder, and a positioning driver, and operates according to external and on-line commands. As a synchronization method using gears as in the experimental apparatus, synchronous rotation can be easily achieved by meshing and connecting a small bevel gear 18 attached to a motor 13 to a large bevel gear 17 whose rotation axis is the vertical shaft 4 . In the embodiment, the type, control method and number of motors to be installed are not limited as long as the motor can be controlled by a sensor.

The amount of deflection due to the fixation of the center of the disk is obtained by the following equation.

The amount of deflection due to fixing the outer circumference of the disk is obtained by the following equation.

1 system motor 2 rotor 3 weight 4 vertical shaft 4a lower end of vertical shaft 5 vibration plate 6 bearing 7 joint 9 horizontal frame 9a impact receiver 10 reaction plate 10a balance line (upper surface of reaction plate)
11 Adjusting ring 12 Slide bearing 13 Motor 15 Support frame 19 Central axis 20 Fixed reference length 21 Fixing bracket 22 Hollow fixing ring 23 Foundation ring





















(1)

Claims (2)

A vibrating device composed of a rotor (2) and a bearing (6) to which a weight (3) and an arm (16) are attached, and a plurality of the vibrating devices at the ends of a disk-like diaphragm (5). Synchronous position control by the system motor (1) through the vibration device and the joint (7), and the vertical axis (4) centered on the center axis (19) of the diaphragm (5) is coupled. The outer circumference of the disc reaction plate (10) is fixed by a base ring (23) and a hollow fixed ring (22), and a support frame (15) is attached to the hollow fixed ring (22) or the reaction plate (10). The vertical shaft (4) fixed and fitted with the adjusting ring (11) is supported by the sliding bearing (12) and the horizontal frame (9), and the vertical shaft (4) is coupled to the center of the reaction plate (10). The vibration plate (5) and the reaction plate (10), which are flexible metal materials, have the same deflection amount due to the rotational stress of the weight (3), or the deflection amount of the reaction plate (10) is equal. is small, and the length from the upper end of the adjustment wheel (11) attached to the vertical shaft (4) to the lower end (4a) of the vertical shaft (4a) is the balance The fixed reference length (20), which is the length up to the line (10a), is matched, and a sine half-pulse wave is generated by impact vibration due to the restoring force of the reaction plate (10), and the vibration plate (5) with the same vibration period is generated. ) is a sine wave and a composite wave to generate inertial force. A rotor (2) in which a small bevel gear (18) attached to a motor (13) is meshed and connected to a large bevel gear (17) whose rotation axis is a vertical shaft (4), and a weight (3) is attached to the rotor (2); 2. A propulsive force generating device by synthetic vibration waves according to claim 1, wherein synchronous position control is performed via a plurality of vibrating devices comprising bearings (6) and joints (7).

















(1)

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