JPH07154959A - Gear engine - Google Patents

Abstract

PURPOSE:To obtain a new driving force by which a gear device itself generates a rotating motive force by a method wherein an impact is applied to the specifically constituted gear device from a vibration generation device which has combined a permanent magnet with an electromagnet. CONSTITUTION:Fixed magnets 31a, 31b are arranged on the upper outside and the lower outside of both bar magnets 27a, 27b which constitute a vibrator bar magnet. Then, they are fixed and bonded to a casing 24, and a magnetic field is constituted. Magnetic axes of the individual magnets 27a, 27b, 31a, 31b and longitudinal axes of arms 10a, 10b, 37a, 37b are constituted in such a way that they are arranged in series at the upper part and the lower part in a standstill. In addition, an output internal gear 4 is attached to a fixed internal gear 1 in an output gear device. Then, an output gear part is constituted of planetrary differential gears which are automatically tightened so as to be a weak restraint and whose diameter is different. Then, a vibrating acceleration force by the vibrator bar magnet due to the self-induction of an electromagnet is applied, and an impact is continued. An impulsive force is generated on an engaged gear face by the blow force, and a rotating power is generated by a dynamic load.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a prime mover, which uses a vibration generator combining permanent magnets and electromagnets to apply a striking force to a specially configured gear device so that the gear device itself generates rotational power. About prime mover. The conventional gear device has been used for a long time as a device that is mounted on another prime mover to transmit power in a variable speed, but the gear device itself has never been taken up as a prime mover that generates rotational power. However, the present invention has developed the principle of the "output gear device" (Japanese Patent Publication No. 47-48130) previously invented by the present inventor, and the "new output gear device" specially constructed by the subsequent research is clean. The focus was on becoming a prime mover that generates rotational power. At the present time, there is a strong demand for clean energy for preventing environmental pollution and global warming, and the present invention has been made to meet this demand. According to the present invention, a plurality of planetary differential gears that are automatically tightened under weak restraint are directly connected to each other by a fixed shaft so as to elastically prevent rotation of the gear members of a fixed member to a gear box, and directly connected to the gear members of an output member. This is a prime mover that constitutes a "new output gear device", and applies a striking force in the circumferential direction to a fixed shaft to generate rotational power by means of a vibration generator composed of a permanent magnet and an electromagnet. When a permanent magnet is suddenly brought close to the magnetic needle,
The needle oscillates left and right in the circumferential direction and vibrates for a while. This phenomenon is caused by changing the magnetic needle to a thick and large bar magnet, and vibrating for a moment when the tip is flipped in the circumferential direction in the magnetic field of a fixed permanent magnet (hereinafter, fixed magnet), and the couple moment generated at that time. Accumulates in the moment of inertia of the bar magnet to generate a striking force. Therefore, according to the present invention, the crank arm of the striking portion is fixed to one end of the crankshaft, and the bar magnet is attached to the boss portion of the other end, in the non-magnetic casing fixed to the side surface of the gear box of the "new output gear device". It is fixed at right angles to the magnetic axis, the iron core arm is fixed to the end surface of the boss portion to form a vibrator bar magnet, and the fixed magnet is fixed to the outside of it to form a strong magnetic field, and to the left and right of the iron core arm tip. A magnetic starting device (vibration generating striking device) is configured by a closed-flow-ring type electromagnet in which a condenser is installed in series in the electric circuit of a solenoid where a protruding and fixed iron core goes in and out, and a vibrator bar magnet is provided by self-induction of the electromagnet. The acceleration force is added to the vibration of the
This is a gear engine that generates rotational power by the impact force and dynamic load generated on the meshing tooth surface by this impact force. Next, the configuration of the present invention will be described with reference to an embodiment. The magnetic actuating device comprises a non-magnetic casing 24, which is fixed to the right side surface of the gear box 6, and a vertical wall which is parallel to the fixed shaft 7 on the inner wall 24 '. Non-magnetic crankshaft 17ab that is evenly arranged and bearing
A bar magnet 27ab is inserted and fixed to the right boss portion 17ab 'of which a vertical axis through hole is provided, and a non-magnetic iron core arm 37ab is fixed to the right end surface of the boss portion 17ab' so as to face each other.
The crank arm 10ab is fixed to the left end of the crankshaft 17ab so as to face outward to form a vibrator bar magnet. Fixed magnets 31ab are equally arranged on the upper and lower outer sides of the two bar magnets 27ab and fixed to the casing 24 to form a magnetic field.
7ab, 31ab magnetic axes and both arms 10ab, 37
The vertical axis of ab is configured to be vertically connected in a stationary state.
Hammer pins 30ab are laterally projected and fixed to the outer ends of the crank arms 10ab to prevent the rotation disc 8 from rotating.
And the striking surface 8ab 'in the right direction of the striking face. Then, half-moon-shaped iron cores 22ab, which are laterally projected and fixed to the adjacent ends of the two iron core arms 37ab, are overlapped and inserted into the left and right solenoids 23ab, and a condenser 39ab is connected in series to the electric path to connect the closed-flow coil. Form an electromagnet. The detent disc 8 having a spline pair on the right end of the fixed shaft 7 has a shock absorber 20 press-fitted into through holes arranged equidistantly and fixed to the right side surface of the gear box 6 by a fixing pin 20 '. Make up. The hammer pin 30ab is provided with a circular arc-shaped long hole in the upper and lower portions of the rotation-stopping disc 8 so that the hammer pin 30ab can swing in the circumferential direction to form a striking portion.
The ab is positioned so as to hit only the right striking surface 8ab 'of the elongated hole to stop the rotation, thereby forming an elastic rotation stopping device.
Further, the new output gear device includes a fixed internal gear 1 which is spline-paired with the left end of a fixed shaft 7 laterally supported by the gear box 6 and is prevented from rotating, and an output shaft 9 cantilevered on the left side surface of the gear box 6. The output internal gears 4 fixed to the right end of the cylindrical shaft portion 9'of the above are arranged in parallel, and the output planetary gears 2.3 having different diameters simultaneously meshed with both internal gears 1 and 4 are idled on the fixed shaft 7. The output gear unit is constituted by a planetary differential gear device of different diameters which are equally arranged on the output planetary carrier 5 and are mounted on the output planetary carrier 5 and are automatically tightened under weak constraint. The output sun gear 14 provided in parallel with the fixed sun gear 11 fixed to the central portion of the fixed shaft 7 is the output internal gear 4
The flange part 4'of the
The interlocking planetary gears 12 and 13 of different diameters that simultaneously mesh with both sun gears 11 and 14 are equally placed on the interlocking planet carrier 15 that is idled on the boss portion of both sun gears 11 and 14, and are axially mounted to weakly restrain them. The interlocking gear part is composed of a planetary differential gear device of different diameter that automatically tightens. Then, both gear parts are constituted by conical gears, and the side in which the output gear parts 1, 2, 3, 4 are arranged in parallel are geared at the large end, and the interlocking gear parts 11, 12, 13, 14 are both sun gears 11, The parallel side of 14 has a small end face, and the interlocking planetary gear 1
The side of the 2 and 13 side by side is geared to the large end face. Then, the coil spring 19 inserted between the boss portion of the rotation stopping disk 8 and the V-shaped clutch 40 presses it in the left direction, and each conical tooth surface is press-fitted in a backless gap to weakly restrain the restraining force. Configure an auto-tight planetary differential gear system. The V-shaped clutch 40ab is provided with V-shaped tooth grooves on both contact end faces and meshes with each other, and the arms 40 project to the outer surfaces of the respective arms 40.
The ab ′ is pulled by the wire rope 54 so that the V tooth surfaces push in the axial direction, and the fixed shaft 7 presses the fixed shaft 7 to the left through the inner ring of the right bearing 7 ′ with the inner wall 24 ′ as a reaction force. Constitute. Next, the gear configuration of the embodiment will be described in detail. As for the number of teeth of both gear portions, the fixed internal gear 1 is Z ₁ , hereinafter, 4 is Z ₄ , 2.3 is Z ₂ · Z ₃ , and the fixed sun. The gear 11 is N ₁₁ , 14 is N ₁₄ , 12 and 13 is N _12.
With N ₁₃ , the gear ratio of the output gear, that is, the speed ratio i
z is To become, Z _2> constructed in different diameters of Z _3, output in respect first output rotation of the gear 4, planet having different diameters which the output planetary gear 2 and 3 revolve in accelerated in the same direction in accordance with iz Configure a differential gear unit. Then, the gear ratio of the interlocking gear, that is, the speed ratio iN is When N ₁₂ <N ₁₃ , the iN has a negative (-) value, and the output planetary gears 12 and 13 follow the iN for one output rotation of the output sun gear 14 and accelerate in the opposite direction. Then, a planetary differential gear device having a different diameter that revolves is constructed. In addition, the meshing radius of each gear is R for the fixed internal gear 1.
_{When 1} , 4 is R ₄ , 2.3 is R ₂ · R ₃ , and the fixed sun gear 11 is r ₁₁ , 14 is r ₁₄ , and 2.3 is r ₂ · r ₃ , the meshing radius of the output gear part is The ratio Rz is The binding force increases as the gear configuration is such that the value of Rz approaches 1, and when the value of Rz is reduced, the binding force decreases and the motor rotates in the forward and reverse directions. According to the tester, Rz≈0.85
By configuring around 0.9, it is possible to configure a planetary differential gear device of different diameters that rotates in the deceleration direction but rotates while weakly restraining and automatically tightening in the acceleration direction. Then, the meshing radius ratio rN of the interlocking gear portion in the speed increasing direction is Therefore, it is possible to configure a planetary differential gear device having different diameters that automatically tightens a weak constraint by configuring the rN value in the same manner as described above. However, this gear portion can be configured so that the number of teeth of the interlocking planetary gears 12 and 13 is larger than that of the sun gears 11 and 14 due to the meshing of the external teeth, and accordingly the difference in the moment of inertia becomes large. Therefore, even when the meshing radius ratio rN is set to the same value as Rz, a restraining force larger than that of the output gear portion is generated due to the slow motion described later. Therefore, the binding force of the new output gear device as a whole becomes a combined force that is automatically tightened by the weak binding of both gear parts. However, the restraint force changes due to the generation of vibration of the gear system and the increase / decrease in the load reversal force, which will be described later. When the meshing radius ratio is set to Rz = 1 = rN, a self-locking planetary differential gear device is obtained, which cannot rotate in the speed increasing direction and cannot be configured as a new output gear device of the gear engine. In the conical gear, when the table of the gear cutting machine is moved in the direction perpendicular to the axis by gear cutting with a hob, the large end face becomes a plus (+) dislocation and the small end face becomes a minus (-) dislocation, and both tooth faces The twist angle of is in the opposite direction,
The tooth trace becomes a special helical gear with a wedge shape. When the gear cutting inclination angle is set to γ degrees, the twist angle β degree on the pitch cylinder becomes β = ± tam ⁻¹ (tamβg · secα), and the meshing pressure angle α when there is no back gap is the axis-perpendicular pressure angle α. _o
And equal ^{α = tam -1 (tamαh · cosγ} ) = α o crimp claw was even to the same meshing movement and spur gear. If the inclination angle γ and the tool pressure angle αh are set so that the twist angle β becomes equal to or larger than the friction angle of the meshing tooth surface, the gear cutting is performed even when a hitting force is applied to the rotation stopping disc 8 of the fixed shaft 7. , Planetary gears 2 that do not bite in the direction of the tooth traces
3, 12, and 13 smoothly rotate and revolve to perform an output action. And β can be obtained from the base cylinder twist angle βg βg = tam ⁻¹ (tamγ · sin α). However, both internal gears 1, 4 are
When the gear blank is tilted by γ degrees and gear cutting is performed by a pinion cutter, a tooth profile error occurs, meshing motion becomes unsmooth, and output efficiency may be extremely deteriorated. Therefore, after finishing cutting, when finish rolling with a die roller of the external tooth of the theoretical tooth profile,
Correcting the tooth profile and making the tooth surface smooth, the output planetary gears 2 and 3 smoothly rotate and revolve to perform output operation with high efficiency. Also, with a special pinion cutter for skiving gear cutting, while moving in the direction perpendicular to the axis, the internal tooth cutting becomes the theoretical tooth profile as if shaving, but since a large force perpendicular to the axis acts on the cutter, it is large. Suitable for large conical internal gears 1 and 4 for engines. Further, if the gear ratios of both gears, that is, the speed ratios iz and iN are made smaller, the output rotation angles of both output gears 4 and 14 due to one impact force w of the hammer pin 30 become larger. However, if the left and right gear trains of different diameters are made to have the tooth profile of the same size and the tooth number ratio is made small, the values of the meshing radius ratios Rz and rN become too small, and an appropriate restraining force may not be obtained. In that case,
By changing the right and left modules of the different diameter gear train to make an appropriate meshing radius difference, it is possible to construct a planetary differential gear device of different diameters that automatically tightens under weak constraint. Next, regarding the embodiment, the impact force F generated on the meshing tooth surface of both fixed gears 1 and 11
To explain the ratio of P and P, the meshing radius R of the fixed internal gear 1
_When the impact force of ₁ is F and the impact force of the meshing radius r ₁₁ of the fixed sun gear 11 is P, the mass m of both gear parts and the turning radius K are shown.
When the moment of inertia of is applied to the rotation stopping disk 8 and the distance h of the striking face 8'from the fixed axis 7 is set to a length of a simple pendulum, the impact force generated on the fixed axis 7 becomes zero. Then, the striking surface 8'becomes a hit. Therefore, the striking force W generated on the striking surface 8 ′ by the striking force w of the hammer pin 30 produces striking forces F and P on the meshing tooth surfaces of the fixed gears 1 and 11. Therefore, the distance from the fixed axis 7 of the center of gravity G, which considers the entire gears including the rotation stopping disk 8 as a double pendulum. And the ratio of the engagement radii R ₁ and r ₁₁ to the impact forces F and P is become. In the embodiment, R ₁ > r ₁₁ is set, and a large impact force F is generated on the meshing tooth surface of R _{1 having} a large meshing radius. Therefore, it is the reason why it is called the output gear unit. Then, a small impact force P is generated on the meshing tooth surface with a small r ₁₁ , which acts in reverse to the tangential force generated on the meshing tooth surface of the conventional speed increasing / decreasing gear device. That is, in the conventional gear device, the conversion force having the same magnitude as the acting force of the meshing tooth surface acts on the shaft center in the same direction, but in the case of the impact force, the impact force generated on the shaft center 7 is generated. Can be configured to zero. In addition, the impulse of the impulse is increased in comparison with the acting force that is not the impulse, and the impulse W,
Other forces can be ignored when dealing with F and P. As described above, the new output gear device of the present invention is different from the conventional gear transmission theory because it operates by the impulse of the impact forces F and P. Next, the structure of automatic tightening with a weak constraint will be described for the embodiment. The planetary gears 2, 3, 12, and 13 of both gears are composed of both internal gears 1 and 4, both sun gears 11 and 14, and left and right gear trains. Mesh on the opposite tooth surface,
Engage on the stride thickness of the intersecting lines of action. Therefore, the tangential force of the meshing tooth surface acts and reacts in the opposite direction on the tooth trace of different diameter difference, and the binding force is generated to automatically tighten in the acceleration direction. Therefore, in both planetary gears 2, 3, 12, and 13, the extremely small meshing resistance caused by the sliding and rolling of the meshing tooth surfaces acts on both ends of the bristle tooth thickness length, so that a large rotation force is generated by a small restraining force. Automatically tighten. Then, as described above, the restraining force can be increased or decreased depending on the configuration of the meshing radius ratios Rz and rN. However, as will be described later, the impact force F, P generated for a moment of impact and the vibration of the gear system change, but the restraining force can be adjusted by increasing or decreasing the crimping force of the conical tooth surface. Therefore, the new output gear device of the present invention can be configured as a gear so as to rotate in the speed-up direction while automatically tightening with a weak constraint when the back gap is engaged. Next, the structure and operation of the magnetic activator of the embodiment will be described. The magnetic pole at the upper end of the upper bar magnet 27ab is set to N.
The upper end of the lower bar magnet 27b adjacent to the lower S pole is the N pole, and the lower end of the upper fixed magnet 31a is the S pole.
When the upper end of the lower fixed magnet 31b is made to be the N pole, the magnets magnetically attract each other in the direction of the magnetic axis, and the oscillator bar magnets stand still in series in the vertical direction. In that stationary state, one bar magnet 2
When one end of 7a is pulled to one side and tilted by θ degrees, the adjacent magnetic pole of the other bar magnet 27a is attracted and tilted in the opposite direction by θ degrees, and when it is suddenly released, it makes a temporary amplitude motion and rapidly decreases the amplitude angle θ. Stop. At this time, bar magnet 27ab of the magnetic moment M is in the magnetic field strength H, each couple moment M _o =
MHsin θ acts, the tilt angle θ becomes maximum at a position of 45 degrees, M _o = zero at the series point of θ zero, and −M _o acts in the opposite direction beyond the series point. couple moment ± M _o to the moment of inertia Im of the interim vibration acts on the forward and reverse. Therefore, when the electromagnet 23ab is energized, the two semi-cylindrical iron cores 22ab together come and go under the attraction and repulsive force of the solenoid 23ab, and the bar magnet 27
In addition to the electromagnetic acceleration force to ab of the couple moment M _o vibrate at high speed. At that time, it becomes the same as the electromotive force of Q / C is reversed due to the quantity of electricity Q charged in the capacitor 39ab having the capacity C during the amplitude, and the attraction force and the repulsive force of the left and right solenoids 23ab during one reciprocating amplitude. Act alternately, and the vibration can be sustained by applying an electromagnetic acceleration force to the oscillator bar magnet.
The electromotive force generated by the self-induction of the obstruction coil is increased as the moving speed of the iron core 22ab, that is, the amplitude speed of the oscillator bar magnet is increased, and the hammer pin 30
The striking force w generated in ab is increased, but the power consumption is reduced. When the amplitude angle θ is in a certain range, the bar magnet 27 having the moment of inertia I has a period of T ′ seconds. Accordingly, the self-induction period ω ′ of the electromagnet is forcibly vibrated in synchronization with the period T of the oscillator bar magnet. But I
Since m> I, the vibration velocity of the oscillator, that is, the impact velocity v
= 1 / T is slightly smaller than v '= 1 / T', but because of the originally high speed, the couple moment _Mo and the electromagnetic acceleration force are accumulated in the inertia moment Im to exert a striking action. ′
A strike force W is generated at. That is, the couple moment M
_o increases and decreases as the amplitude angle θ changes with time, but a large M _o at the dead point at which the engine starts to the right of the impact.
Accumulates in the moment of inertia Im, an electromagnetic acceleration force is applied to this, and a striking force w acts on the hammer pin 30 to strike the striking surface 8'at a velocity v. Since the fixed shaft 7 is elastically prevented from rotating, the striking parts 8'and 30 move together in the striking direction for t seconds after the collision, and the velocity u after the collision momentarily follows the restitution coefficient. Decreases and receives repulsive force. at the same time,
Amplitude returns to the left couple moment M _o and the electromagnetic accelerating force in the opposite direction is exerted, again couple moments reach the left side of the dead center (+ M _o) and electromagnetic accelerating force accelerates amplitude acts rightward , Hitting action. At that time, hammer pin 3 of speed v
0 collides with the striking surface 8'of zero speed, and the speed difference (v-
u) loses kinetic energy, but to the repulsive force of the elastic detent device, the electromagnetic acceleration force to the left and the couple moment (-
_Mo ) is added and the amplitude of the return is continuously increased. When the oscillator bar magnet on the upper portion accelerates to the right and strikes, the oscillator rod magnet on the lower part returns to the left and swings, and when the oscillator rod magnet moves in the opposite direction, the hammer pin 30b on the lower portion strikes. Since it works, a double strike force W is generated during one round trip.

Even in the case of the same bar magnet 27, if the magnetic moment of the fixed magnet 31ab is increased, the impact force W increases. However, if the striking position of the striking surface 8'is near the dead point to the right,
The generation of W is reduced, and the return amplitude force is reduced when it is brought too close to the series position. Therefore, a large striking force W can be generated at an intermediate position between both points. Next, the operation of the gear engine of the present invention will be described with reference to an embodiment. The impact force w of the magnetic starter causes a fluctuating load on the meshing tooth surface of the new output gear device due to impact forces F and P and vibration of the gear system. However, at the same time, both planetary gears 2, 3, 12 and 13 are momentarily accelerated in the direction of the respective gear ratios for a moment to rotate and revolve, and both output gears 4 and 14 are driven in the direction of striking force w. The output rotates after decelerating to. At that time, the two planetary gears 2, 3, 12, and 13 rotate at the moment of impact by using the meshing tooth surfaces of the two output gears 4 and 14 as a reaction force to rotate at the same time, and at the same time, due to the revolving motion, the two fixed gears 1 and 11 rotate.
The output gears 4 and 14 are decelerated and rotated in the direction of the striking force w by using the meshing tooth surface of as a reaction force for output rotation. Therefore, the speed ratio i
z and iN act at the same time, and the interlocking planetary gear 12.1
3 revolves to the left, and the output planetary gears 2 and 3 revolve to the right to act as outputs. Therefore, at each moment of impact, the fixed gears 1 and 11 are locked by the detent devices 7 and 8,
When the vibration amplitude τ slightly oscillates in the circumferential direction in accordance with the vibration cycle τ of 20, and τ is configured to be smaller than the cycle T of the oscillator bar magnet, the hammer pin 30 is repulsed together with both the fixed gears 1 and 11 and oscillates back to the left. . Then, the output planetary gears 2 and 3 accelerate for a moment and then rotate counterclockwise, while accelerating to the right in accordance with the speed increasing ratio iz and revolving, thereby moving the output internal gear 4 to the reduction ratio 1 / iz. Accordingly, the rotation is decelerated in the right direction, and at the moment when the strike force F disappears, the restraining force prevents the reverse rotation, and the output rotates in one direction. At the same time, the interlocking planetary gears 12 and 13 continuously rotate counterclockwise every time a slight amplitude is applied to the forward and reverse directions,
It revolves in the leftward direction according to the speed increasing ratio iN, and outputs the output sun gear 14 after decelerating and rotating in the rightward direction according to the speed reducing ratio 1 / iN. Therefore, since both output gears 4 and 14 of the same rotating body have a large moment of inertia of the interlocking planetary gears 12 and 13, and a rotation force and a restraining force are generated on the same meshing tooth surface, one reciprocation of a small amplitude occurs. It continuously revolves in the left direction and rotates in the right direction. Strictly speaking, at the moment when the hammering force P disappears, the gear trains 11, 12, 13, 14 of the interlocking gear unit are integrated into a glued state due to the restraining force, and a revolving motion of rotating to the left also occurs. Since the vibration of the gear system is generated during the continuous leftward rotation of the planetary gears 12 and 13, a rotation force due to a moment of inertia that does not depend on the impact force P is generated, and a moment of force to the right (= inertia moment × angular acceleration). ) Acts to rotate the output. This effect is clear in the following. That is, when the arm 4O'ab of the V-shaped clutch 40ab is pulled and the conical tooth surface pressure is increased, the restraining force is increased and the reverse rotation due to the load is prevented. At the same time, the revolution torques of both planetary gears 2.3, 12 and 13 increase and the output torques of both output gears 4 and 14 increase, while the output rotation speed slightly decreases. When the electric power supplied to the electromagnet is increased, the striking forces F and P are increased, and the output torque and the output rotation speed are increased and output is performed. Next, the principle of the new output gear device will be explained.All gear devices, when hitting the airframe strongly at rest, momentarily vibrate at the same natural frequency of the gear system as in operation, causing the meshing teeth. A static load is applied to the surface and a fluctuating load (hereinafter referred to as a dynamic load) is applied to the surface, and the maximum occurs at the resonance point in the natural frequency range. When the gear portion is directly hit, a small impact causes resonance and a large dynamic load is generated. In particular, the planetary differential gear device is apt to resonate due to the primary deceleration, and has a characteristic that the ratio of the rotation torque and the constraint torque acting on the planetary gears 2, 3, 12, and 13 changes for a moment of impact. At that time, the large and small gears meshing with each other move relative to each other in the circumferential direction in reverse proportion to their respective inertia moments, and the meshing tooth surfaces transiently respond to each other to generate a dynamic load, The theoretical maximum is 2. At that time, the large and small gears move slowly with respect to each other, the gear with the smaller number of teeth and the smaller moment of inertia is on the lead side, and the gear with the larger number of teeth and the larger moment of inertia is on the lag side and meshes. The new output gear device configured as described above by a plurality of planetary differential gear devices that move and are automatically tightened in a weakly constrained state is rotated by the rotation force generated by the impact forces F and P and the dynamic load. At the same time
Reverse rotation is prevented by the restraint force, both acting forces are instantaneously generated on the same meshing tooth surface, and output rotation is performed in one direction. that time,
It is easy to think that the planetary gears 2, 3, 12, and 13 of both gears are free to rotate, but in reality, they are self-controlled by the rotation torque and the constraint torque peculiar to the planetary differential gear device, Rotate and revolve while restraining. Then, both torques are generated on the same meshing tooth surface, the rotation restraint torque ratio (ratio of rotation torque and restraint torque) changes for a moment of impact, and each tooth is changed by the rotation force generated by the impact forces F and P. It rotates in the direction of a number ratio, and at the moment when the impact forces F and P are attenuated, it is restrained to prevent reverse rotation, and self-controlled to rotate and revolve. That is, in all the planetary motion devices, when the planet wheel rotates by the angle θp due to the rotation angle θd of the motor, the planet wheel is pulled back from the rotation angle θp by the revolution angle θ _o (θp−θ).
_o ) Only spins and makes a planetary motion. If it is configured as a gear device, the gear meshing motion There is a transfer component due to the revolution angular velocity ω _o = θ _o , which is not accompanied, and the revolution component generated in the planetary gear by the motive force τd ωd. A velocity ω _o ² occurs. And the revolution angular acceleration ω
_o ² becomes a constant in the case of a single planetary gear device, but becomes a variable in a planetary differential gear device, and due to the generation of dynamic load, ω
The moment of force due to _o ² increases and acts, and the output rotates against the external force. Therefore, in the new output gear device of the present invention, when the dynamic load resonates on each meshing tooth surface due to the striking force w, the rotation restraint torque ratio of both planetary gears 2, 3, 12, and 13 changes for a moment, and at the same time, The repulsive angular acceleration ω _o ² acts due to the generated striking forces F and P to generate a moment of force in the revolving motion, which acts and reacts in the direction of the respective speed ratios Rz · iN of both gear parts, resulting in both outputs. The gears 4 and 14 strike the force F,
The output rotates against the external force by decelerating in the direction of P. However, when there is only one set of planetary differential gears, each gear makes relative movement in the circumferential direction for a moment of impact, but since there is no reaction force, it may oscillate while maintaining neutrality, and output rotation may occur. Can not. However, if an elastic force storage device is incorporated like the “output gear device”, the torque ratio will increase due to the revolution angular acceleration ω _o ^{2 for} a moment of impact. Rotate. The striking force in this case has no directivity, and the output rotates even when the machine body is striked in any direction in the front, rear, left, and right directions, or when the mounting base is similarly striking. However, the "new output gear device" of the gear engine of the present invention generates rotational power without an elastic force storage device, and the striking force w has directionality, and the fixed shaft 7 that is elastically stopped. The rotational power cannot be generated unless the striking force w is applied in the meshing direction of the gear train. For example, if one of both gears is removed and a striking force w is applied to the striking surface 8 ', it is impossible to generate rotational power. Also, in the case of only the output gear part,
The output planetary gears 2 and 3 are on the advancing side, and the elastic detent device causes a slight amplitude, but the output planetary gears 2 and 3 are kept neutral and the output does not rotate. And in the case of only the interlocking gear part, the interlocking planetary gear 12
・ 13 becomes a delay side and slightly oscillates, and at the slow speed, it oscillates to the left and right in the circumferential direction, but keeps neutral and does not rotate the output. At this time, it is possible to see how the interlocking planetary gears 12 and 13 move relative to each other in the revolving direction due to the repulsion of the meshing tooth surfaces. Further, the vibration of the gear system is a vibrating body of the coefficient excitation type which is generated by the change in tooth stiffness, and therefore, even when the striking force w becomes half or less than the rated value, the output resonates and rotates. However, the dynamic load generation rate (dynamic load rate) converges when it reaches a certain value, and does not increase any further. At that time, the output increase due to the fluctuating load disappears, and the impact force F,
Increases as P increases. Therefore, if it is configured so that the output acts under the allowable tooth surface pressure, the output rotates sensitively.
However, rotation energy cannot be generated only by the new output gear device. Therefore, the present invention applies an electromagnetic acceleration force by the self-induction of a closed-flow-ring type electromagnet to a phenomenon in which a bar magnet rapidly swings in a magnetic field due to a large magnetic energy previously given to a magnetic activator. The striking force w generated by
And a dynamic load is generated, and the moments of the forces generated in both the output and interlocking gear parts interact to generate rotational power. For example, when grasping the central portion of a thick and large bar magnet and performing amplitude movement in the circumferential direction, a large inertial resistance is felt. The resistance increases as the amplitude velocity increases. However, if this movement is performed with the magnetic field of the fixed magnet, the resistance is lost and the vibration can be swung lightly at high speed. At that time, when the non-magnetic body is hit with the tip of the bar magnet, a large impact force is generated.
This reduced angular momentum stores the moment of inertia of the bar magnet and strikes it to generate a large striking force to generate rotational power. Further, when the bar magnet of the embodiment is replaced with an iron bar to form a vibrator, the iron bar is magnetized by the strong fixed magnet, and the iron bar is oscillated and impacted in the same manner as described above to generate rotational power. However, the striking force w is higher than that of the permanent magnet bar magnet.
Is less likely to occur. Further, the permanent magnet not only demagnetizes while being left unattended, but also quickly demagnetizes when vibration is applied. Therefore, it is possible to re-magnetize and maintain the generation of the rotational power for a long time. However, a large amount of electric energy is required for the magnetization, and the magnetic energy and the electric power for the electromagnetic accelerating force given in advance serve as an energy source to generate clean rotational power. Moreover, in the case of a closed-flow ring type electromagnet, the electromotive force increases as the iron core moves in and out faster, and it consumes less power for the electromagnet accelerating force supplied by a solar cell, dry cell, or battery. become. Further, in the gear engine of the present invention, a plurality of magnetic actuation devices are mounted in different phases so that the striking position is shifted, and the gear engine is multi-connected to increase the number of striking per unit time and increase the output rotation speed to increase the output. I can do things. And the gear engine of the present invention not only directly drives other machines,
A generator can be installed to generate clean power.

[Brief description of drawings]

FIG. 1 is a front sectional view showing the whole of the present invention. FIG. 2 is a right side view showing the inside of the magnetic starting device with the cover removed. FIG. 3 is a perspective view showing a magnetic starting device. FIG. 4 is a perspective view of a V-shaped clutch. 1. Fixed internal gear 11. Fixed sun gear 24. Casing 2. Output planetary gear 11. ′ Boss part 24. ′
Middle wall 3. 〃 12. Interlocking planetary gear 24c
Cover 4. Output internal gear 13. 〃 27. Bar magnet 4. ′ Flange section 14. Output sun gear 30. Hammer pin 5. Output planet carrier 15. Interlocking planet carrier 31. Fixed magnet 6. Gear box 17. Crankshaft 37. Iron core arm 7. Fixed shaft 17 'Boss 39. Condenser 7. ′ Shaft receiving 19. Coil spring 40. V-shaped clutch 8. Non-rotating disc 20. Shock absorber 8. 'Striking surface 20. 'Fixing pin 40. ′
Arm 9. Output shaft 22. Iron core 54. Wire rope 9. ′ Cylindrical shaft 23. Solenoid 10. Crank arm

Claims (1)

[Claims] A bar magnet is fixed to the other end of the crankshaft of a non-magnetic material with a crank arm fixed to one end at a right angle to the magnetic axis, and an iron core arm is fixed to the side surface of the other end to form a vibrator bar magnet. Alternatively, a plurality of non-magnetic casings are supported parallel to the fixed shaft, and the fixed magnets are fixed to the casing outside the magnetic poles of the bar magnets to form a magnetic field. A magnetic starter is composed of a closed-flow wheel electromagnet with a condenser installed in series in the electric path of a solenoid that moves in and out, and it is attached to the detent part of the fixed shaft, and a plurality of planetary differential gears are automatically tightened with weak constraints. The gear members of the fixed member are directly connected by a fixed shaft to elastically prevent rotation in the gear box, and the gear members of the output member are directly connected to form a new output gear device, and the vibrator rod is self-induced by the electromagnet. The impact force generated by adding electromagnetic acceleration force to the stone's amplitude motion simultaneously generates an impact force and a dynamic load on the meshing tooth surface, and the output rotates. A gear engine that produces rotational power.