JP7087216B1 - Propulsion force generator by synthetic vibration wave - Google Patents

Abstract

PROBLEM TO BE SOLVED: To match the vibration period of a sine wave of a vibrating plate and a sine half-pulse wave of a reaction plate to a synthetic vibration on the ground and in space without requiring a reaction force by a jet substance such as fossil fuel to the outside of the device. Generates an inertial force. SOLUTION: A plurality of vibrating devices for generating an unbalanced centrifugal force by a weight 3 are evenly arranged on a vibrating plate 5 of a disk, and a system motor 1 controls a synchronous position to control the vibrating plate 5 and a vertical axis 4. The vertical axis 4 is made upright without being coupled to the center of the reaction plate 10 of the disk fixed and the outer circumference is fixed, and the vibrating plate 5 and the reaction plate 10 which are flexible metal materials are equally interlocked by the rotational stress of the weight 3. By setting the length from the upper end of the adjusting nut 11 to the lower end 4a of the vertical axis as the fixed reference length and controlling the vibration range of the reaction plate 10, the vibration plate 10 has the same vibration period as the sinusoidal wave of the vibration plate 5. The combined wave of the sine half-pulse wave by the restoring force makes it possible to generate the propulsive force by the inertial force. [Selection diagram] Fig. 1

Description

The present invention relates to a propulsion force generator that obtains propulsion force by the inertial force of synthetic wave vibration by a diaphragm and a reaction plate without discharging jets to the outside, unlike a rocket engine or the like.

In order to reach outer space from the ground and operate, the earth's gravity escape velocity is required, and in order to obtain acceleration, a large amount of launch fuel is required to propel the rocket. In addition, jet engines of airplanes emit a large amount of high-temperature gas, which is also a cause of global warming. In addition, these aircraft cannot fly depending on the weather conditions and are often canceled.

As a remedy for this, we provide a propulsion force generator using synthetic vibration waves, which does not require a reaction due to jets on the outside of the device, has an inertial force acting only in a specific direction, and is extremely safe.

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

Vibrations are substantive waves that affect any object. For example, it is possible to combine an A vibration wave traveling in a medium and a B vibration wave traveling from the opposite direction, and even after the synthesis, unlike collisions between objects, each other's waves proceed without disappearing. It is also proved as wave independence that the combined vibration of two waves is transmitted to the medium at the time of synthesis.

There is a wave called an impact pulse, and in a dynamical system, it is a wave that gives an excessive dynamic disturbance to an object. This is applied as a wave effect in impact testing of electronic products used in electronic devices, automobiles, aerospace industry, and the like.
Among several types of impact pulses, a sine and cosine half-pulse wave is a half-cycle waveform of half a sine wave, that is, only a positive part or a negative part.
An object of the present invention is to amplify vibration energy in a specific direction by synthesizing a sine and cosine half-pulse wave with a sine wave, and to obtain a propulsive force by an inertial force.

In order to form the above-mentioned combined wave, the subject is a method of efficiently combining both by generating a sine half-pulse wave by applying the vibration of the sine wave generated in the diaphragm and the restoring force of the reaction plate.

The invention for solving the above-mentioned problems is a vibrating device for generating an unbalanced centrifugal force composed of a rotor 2 to which a weight 3 and an arm 16 are attached and a bearing 6, and a disk having a plurality of vibrating devices. It is evenly arranged at the end of the vibrating plate 5, and the vibrating device is controlled in synchronization by the system motor 1 connected by the joint 7, and the center of the vibrating plate 5 is connected to the vertical axis 4 centered on the central axis 19 to form a disk. The support frame 15 is fixed to the hollow fixing ring 22 for fixing the outer periphery of the reaction plate 10 or the reaction plate 10, the adjusting wheel 11 is attached to the vertical shaft 4, and the vertical shaft 4 is supported by the sliding bearing 12 and the horizontal frame 9. The length from the upper end of the adjusting wheel 11 to the lower end 4a of the vertical axis is the length from the impact receiving 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. Match the fixed reference length 20 and make the vertical axis 4 stand upright without being coupled to the center of the reaction plate 10.

The vibrating plate 5 and the reaction plate 10 are flexible metal materials, mainly iron-based metal materials, and the relative deflection amount with respect to both centers to which stress is applied is the deflection amount of the vibration plate 5 and the deflection of the reaction plate 10. Both sizes and thicknesses are determined so that the amounts are equal or the amount of deflection of the reaction plate 10 is small. According to Hooke's law, the amount of deflection due to stress and the vibration amplitude are in the same relationship.

When the weight 3 of the vibrating device is rotationally synchronized by the system motor 1, the vibrating plate 5 vibrates in a sine wave due to centrifugal force, and the reaction plate 10 in contact with the vertical axis 4 also vibrates under the force, and the amount of deflection of both is equal. In this case, the vibrating plate 5 and the reaction plate 10 vibrate with the same amplitude and period, and the vertical axis 4 and the reaction plate 10 vibrate in close contact with each other.

When the adjusting 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 stop momentarily at the equilibrium line 10a and cannot physically vibrate to the ascending side. The shock vibration due to the restoring force of the reaction plate 10 having the same amplitude and period as the vibrating plate 5 becomes a sine half pulse wave which is a half wavelength of the sine wave and propagates on the vertical axis 4, and the sine wave and the vibration period of the vibrating plate 5 Will form an equal composite wave.

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

The metal material used for the vibrating plate 5 and the reaction plate 10 may be a combination of metal materials having slightly different elastic moduli such as Young's modulus and tensile strength as long as they vibrate in a sinusoidal wave. If they are equal, or if the amount of deflection of the reaction plate 10 is small, both vibration cycles will be the same.

As a configuration for generating a sine half-pulse wave, the length from the upper end of the adjusting wheel 11 attached to the vertical axis 4 to the lower end 4a of the vertical axis is set from the impact receiver 9a at the lower end of the horizontal frame 9 intersecting the central axis 19 to the central axis as well. By matching with the fixed reference length 20 which is the length of the reaction plate 10 intersecting with 19 up to the equilibrium line 10a (upper surface of the reaction plate), the vibration range of the reaction plate 10 is physically limited by the vertical axis 4, and the reaction plate 10 is physically limited. 10 vibrates only below the equilibrium line 10a and cannot vibrate above it.

Since the vertical axis 4 and the reaction plate 10 are not coupled, even if the diaphragm 5 vibrates to the ascending side from the equilibrium state due to the centrifugal force of the weight 3, the reaction plate 10 is not affected by the vibration and the equilibrium line 10a is not affected. The vertical axis 4 and the reaction plate 10 vibrate in close contact with each other in the lower range.

Therefore, when the adjusting wheel 11 attached to the vertical axis 4 impacts the impact receiver 9a due to the restoring force of the reaction plate 10, the impact force becomes a sine half pulse wave corresponding to the half wavelength of the sine wave and propagates on the vertical axis 4 to vibrate. It is combined with the sine wave of the plate 5 to generate an inertial force.

When the amplitude of the reaction plate 10 is smaller than the amplitude of the diaphragm 5, the vertical axis 4 and the reaction plate 10 vibrate in close contact with each other because the vibration cycle of the diaphragm 5 is not delayed even if the wavelength of the reaction plate 10 is shortened. Generates inertial force.

However, if the amplitude of the reaction plate 10 is larger than that of the diaphragm 5, the vibration cycle becomes longer and delayed, and the vibrations do not match. Therefore, the diaphragm 5 and the reaction plate 10 are metal materials having the same characteristics such as elastic modulus, and when the deflection amounts of both are matched, the vibration periods are also matched, resulting in efficient synthetic wave vibration.

FIG. 1 is a front view showing an embodiment of the present invention. FIG. 2 is a front view showing an embodiment of the present invention. It is explanatory drawing of the composite wave by a sine wave and a sine half pulse wave. It is a perspective view of an experimental apparatus. It is a figure which shows the fixing state of the reaction plate by a hollow fixing ring. It is a figure which shows the synthesis point of a sine wave and a sine half pulse wave.

Hereinafter, examples will be described in detail based on the experimental results.

Experimental Example 1
FIG. 4 shows the experimental apparatus according to the present invention, in which SPCC (cold rolled mild steel plate), which is an iron-based metal material, was used for the diaphragm 5 and the reaction plate 10, both of which are disks. In the case of the vibrating plate 5, the formula for calculating the deflection of the metal material is center concentrated load / formula 1 in which the center of the disk is fixed to the vertical axis 4. Center concentrated load fixed around several places by 21 ・ In the formula 2, stress concentrates on the center of the disk.

In the experimental device, in order to rotate and synchronize the weight 3 of the arm 16 attached to the rotor 2, the small bearing gear 18 attached to the motor 13 is engaged with the large bearing gear 17 having the vertical axis 4 as the rotation axis, and the joint 7 is engaged. The bearing 6 is rotated through the bearing 6. Three of these vibrating devices are evenly arranged on the vibrating plate 5 of the disk, the center of the vibrating plate 5 is connected to the vertical axis 4, the support frame 15 is fixed to the reaction plate 10 of the disk, and the adjusting wheel 11 is provided. The attached vertical shaft 4 is supported by the sliding bearing 12 and the horizontal frame 9, and is configured to stand upright without being coupled to the center of the reaction plate 10.

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

In order to install the vibration device and the motor 13 composed of the three rotors 2 and the bearing 6, the diameter of the diaphragm 5 is 400 mm and the thickness is 2.0 mm, and the reaction plate 10 is made of a material having a diameter of 300 mm and a thickness of 1.2 mm. did. If the diameter of the recoil plate 10 is 296 mm, the amount of deflection of both can be theoretically matched, and when a stress of 200 N is applied, the amount of relative deflection with respect to the central axis 19 is 2.75 mm. .. Further, the stress of 400 N is 5.51 mm, and the stress of 800 N is 11.03 mm, and the amount of deflection is always the same.

Young's modulus (longitudinal elastic modulus) of a metal material has the following relationship.
Young's modulus (E) = stress (σ) / strain (ε)
The elastic modulus such as Young's modulus of the diaphragm 5 and the reaction plate 10 is the same metal material and is equal. Further, the stress due to the centrifugal force applied to both is equal because they are interlocked by the vertical axis 4. 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 plate thickness and size are appropriate, the relative deflection amount with respect to the central axis 19 becomes equal with the change in stress, and the diaphragm 5 and the reaction plate 10 vibrate in a relationship in which the vibration amplitude and the vibration cycle are always equal.

The vibration acceleration of the vibrating plate 5 at the time of natural vibration is 10.1 m / sec ² , which is slightly larger than the gravitational acceleration. It was too 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 center of the diaphragm 5 is coupled to the vertical axis 4, there is damping, and the external force of the motor 13 acts at a speed faster than the natural vibration, resulting in a phase delay.

The experimental device was installed on the electronic measuring instrument, and the outer periphery of the reaction plate 10 was fixed to the top plate of the electronic measuring instrument at several points with the 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 be described below with reference to FIGS. 1 and 2 showing an embodiment of the present invention.
The vibrating device including the rotor 2 and the bearing 6, the vibrating plate 5, and the reaction plate 10 are the same as the experimental device. In this embodiment, the bearing of the slide bearing 12 of the experimental device has been improved to a slide unit suitable for vertical movement.

Further, the reaction plate 10 of the disk is fixed by the foundation ring 23 and the 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 the sliding bearing 12 and the lateral. The vertical axis 4 supported by the frame 9 and to which the adjusting ring 11 is attached stands upright without being connected to the center of the reaction plate 10.

If the length of the fixed reference length 20 which is the length from the impact receiving 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 recoil The length from the lower end 4a of the vertical shaft in contact with the plate 10 to the upper end of the adjusting wheel 11 is adjusted to 200 mm and fixed. Further, when the diaphragm 5 to which the vibrating device or the like is attached is installed on the upper side of the vertical shaft 4 with the fixing nut 8, even if the adjusting wheel 11 and the impact receiving 9a are bent due to the load, the adjustment is not performed. Even if bending is caused by the influence of gravity, vibration acceleration (restoring force) faster than that is generated in the reaction plate 10, and this bending is eliminated.

Four system motors 1 arranged on the diaphragm 5 are evenly arranged, and the hollow fixing ring 22 of the device is fixed to the outside by the fixing screw 24.

When the apparatus of the present embodiment having the above configuration is started, the diaphragm 5 is bent by the centrifugal force of the weight 3 and vibrates in a sine wave, and at the same time, the reaction plate 10 in close contact with the vertical axis 4 also vibrates in conjunction with it. do. The moment the vertical axis 4 vibrates from the valley to the mountain of the vibration waveform due to the restoring force of the reaction plate 10, and the adjusting wheel 11 attached to the vertical axis 4 impacts the impact receiver 9a at the lower end of the horizontal frame 9, the reaction plate 10 and the vertical The lower end 4a of the shaft stops momentarily at the equilibrium line 10a.

Therefore, the recoil plate 10 does not bend and vibrate to the ascending side, and when the weight 3 of the rotor 2 further rotates by 180 °, the vertical axis 4 starts to descend again and the recoil plate 10 bends downward. Become.

Further, when the vibration acceleration is amplified more than the gravitational acceleration and the reaction plate 10 receives vibration from the vertical axis 4, the vibration energy due to the centrifugal force of the weight 3 is accumulated in the reaction plate 10. Since the amount of deflection and the frequency of the diaphragm 5 and the reaction plate 10 are the same, the vibration amplitude and the vibration speed of both are also the same.

Therefore, the reaction plate 10 and the vertical shaft 4 vibrate in close contact with each other, and when the adjusting wheel 11 attached to the vertical shaft 4 by the restoring force of the reaction plate 10 impacts the impact receiver 9a at the lower end of the horizontal frame 9, this impact vibration is vertical. It propagates through the shaft 4 and propagates to the vibrating plate 5.

The impact vibration of the reaction plate 10 is a one-sided amplitude that does not vibrate upward, and has only the element of the positive part that is the force in the ascending direction. It can be called a wave.

Since this sine half pulse wave coincides with the vibration period of the sine wave of the vibrating plate 5, both vibrating waves become a combined vibration wave at the vibrating plate 5 and a propulsive force due to an inertial force is generated on the upper side.

FIGS. 3 (a), 3 (b) and 3 (c) show a series of formation processes of the synthetic wave.
(A) shows a situation in which 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 adjusting screw 11 impacts the impact receiver 9a due to the restoring force of the reaction plate 10 and the sine half-pulse wave propagates on the vertical axis 4 and advances to the bearing 6 side.
(C) shows the direction in which the inertial force is generated by combining both vibration waves.

FIG. 5 shows a fixing state of the recoil plate 10 by the hollow fixing ring 22.
(A) is a perspective view of the hollow fixing ring 22.
(B) is the above sectional view.

6 (a) and 6 (b) are diagrams showing the top composite points where the sine wave and the sine half pulse wave overlap. It is combined only between the straight line of the bearing 6 and the vertical axis 4 on which the force acts at the points where the vibration cycles match.
(A) shows a case where three vibration devices such as a bearing 6 are installed.
(B) shows the case where four of the above devices are installed.

The propulsive force observed by the experimental device is such that the mass of the device 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 is rotated by the rotational couple of the weight 3, it is stabilized by providing a detent to suppress the end portion of the diaphragm 5.

Experimental Example 2
The vibrating device and the vibrating plate 5 including the rotor 2 and the bearing 6 were the same devices up to Experimental Example 1 and subsequent Experimental Example 4, and only the reaction plate 10 was replaced in the experiment. With the SPCC metal material having a diameter of the reaction plate 10 of 300 mm, which is the same as that of Experimental Example 1, and a thickness of 1.0 mm, the static deflection amount is 4.88 mm, which is larger than the deflection amount 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. The recoil plates 10 having a larger amount of deflection than the diaphragm 5 do not have the same period.

Experimental Example 3
With the SPCC metal material having a diameter of 300 mm and a thickness of 1.6 mm of the reaction plate 10, propulsive force is generated even if the amount of deflection is 1.19 mm. This is because both are made of the same metal and have the same elasticity, so that the reaction plate 10 vibrates in close contact with the vertical axis 4, and a sine and cosine half-pulse wave having a short wavelength is generated in proportion to the amplitude. Since this sine and cosine half pulse wave has the same period as the sine wave of the diaphragm 5 even if the amplitude is different, it is 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 that of Experimental Example 1 was observed although it was unstable. Theoretically, if the diameter of the reaction plate 10 is 454 mm, the amount of deflection is 2.73 mm, which is the same as that of the diaphragm 5, and the mass increases, so that the restoring force also increases.

Experimental Example 4
The recoil plate 10 was tested on a stainless steel plate (SUS304) having a diameter of 300 mm and a thickness of 1.5 mm. The amount of static deflection is 1.45 mm, and the tensile strength of the SPCC material is 270 MPa, while that of the stainless steel plate is 520 MPa, which is about twice as different. There are signs that propulsion will occur at the beginning of the vibration, but it will soon become unobservable. It is difficult for the dynamic bending velocities to match for materials with greatly different tensile strengths. However, since it does not exceed the elastic limit, when the diameter is 414 mm, the amount of deflection becomes 2.77 mm and the amplitudes match.

From the above experimental results, the material used for the diaphragm 5 and the reaction plate 10 may be a combination of metal materials having slightly different Young's modulus and elastic modulus of tensile strength, and when both bending amounts are equal, efficient propulsion force is obtained. It can be said that it occurs.

In FIGS. 1 and 2 as examples, the system motor 1 that controls the cycle-synchronous position of the weight 3 has a built-in motor, an encoder, and a positioning driver, and operates by an external command and an online command. Further, as a synchronization method using gears as in the experimental device, if the small bevel gear 18 attached to the motor 13 is engaged with the large bevel gear 17 having the vertical axis 4 as the rotation axis, the synchronous rotation can be easily performed. As long as the motor can be controlled by the sensor, the type, control method, and number of installed motors are not limited in the embodiments.

The amount of deflection due to fixing the center of the disk is calculated by the following equation.

The amount of bending due to fixing the outer circumference of the disk is calculated by the following equation.

1 System motor 2 Rotor 3 Weight 4 Vertical axis 4a Vertical axis lower end 5 Diaphragm 6 Bearing 7 Joint 9 Horizontal frame 9a Impact receiver 10 Reaction plate 10a Balance line (upper surface of reaction plate)
11 Adjusting wheel 12 Plain bearing 13 Motor 15 Support frame 19 Central shaft 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 rotor of the vibrating device (5) at the end of a vibrating plate (5) which is a disk. A plurality of 2) are evenly arranged vertically, the synchronous position is controlled by the system motor (1) via the vibrating device and the joint (7), and the center of the vibrating plate (5) and the central axis (19) are used as the axis. The vertical axis (4) is connected, and the outer periphery of the reaction plate (10) of the disk is fixed by the foundation ring (23) and the hollow fixing ring (22), and the hollow fixing ring (22) or the reaction plate (10) is fixed. ) Is fixed to the support frame (15), the horizontal frame (9) is further attached, and the vertical axis (4) to which the adjusting wheel (11) is attached is supported by the sliding bearing (12) and the horizontal frame (9). Then, the vertical axis (4) is made to stand upright without being coupled to the center of the reaction plate (10), and the vibration plate (5) and the reaction plate (10), which are flexible metal materials, are formed by a weight (3). The relative deflection amount with respect to the central axis (19) due to the rotational stress of the above is equal, or the deflection amount of the reaction plate (10) is small, and the upper end of the adjusting wheel (11) attached to the vertical axis (4). The length from the lower end of the vertical axis (4a) to the equilibrium line (10a) on the upper surface of the reaction plate (10 ) from the impact receiver (9a) at the lower end of the horizontal frame (9) intersecting the central axis (19). The vibration range of the reaction plate (10) is physically limited by matching the fixed reference length (20), which is the length, and the vibration plate (5) is bent by the centrifugal force of the weight (3). The reaction plate (10) that vibrates in a sinusoidal manner and at the same time vibrates in conjunction with the reaction plate (10) that is in close contact with the vertical axis (4). A propulsion force generator using a synthetic vibration wave that impacts a receiver (9a) to generate a sine half-pulse wave and becomes a combined wave with the sine wave of the vibrating plate (5) having the same vibration period to generate an inertial force. A small bearing gear (18) attached to the rotating shafts of a plurality of motors (13) is engaged and connected to a large bearing gear (17) having a vertical axis (4) as a rotating shaft, and a weight (3) and an arm (16 ) are connected. The propulsion force generating device by the synthetic vibration wave according to claim 1, wherein the synchronous position is controlled via a joint (7) and a plurality of vibrating devices including a rotor (2) and a bearing (6) to which the ) is attached.

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