Patent Application
20140298981
The invention relates to the field of engineering and is associated with unit of the rotary motion power devices (energy generators), in particular inertial systems of energy storage/conversion, and can be used to drive various machines and mechanisms.
There are enough developed designs of inertial energy converters using inertia force, generated by rotating body, in order to save electrical energy consumed by electric motor.
One of the known is Inertial drive device (patent RU No. 2076241, 1997) which constitutes a structure in which rotating in one plane unbalance loads execute reciprocating motion and provide a continuous unidirectional action of these loads' inertial force. The device uses a geometric property of circles inscribed in one another with loads with their diameters in ratio of 1:2 and reverberating in one another without slipping. Main fault of the device is the use in its design of the planetary transmission (the most energy intensive mechanical transmission) requiring highly accurate design solutions and very limited in speed characteristics. Since the power of the engine to drive the device is spent only for the rotation of the planetary transmission, saving of the electrical energy, consumed by it, is very small in practice.
Also is known Inertial transmission (patent RU No. 2354873, 2009), in which design inertial mechanism is made in form of two similar in construction hollow rings of rectangular section, in which internal space is filled with mercury. Pumps, which move mercury at high speed inside the rings, are fixed on the widened parts of the rings. When mercury moves, inertial forces F and F1 of different values and operating in opposite directions occur. These forces, balanced in no way and acting, in different directions, create the couple of forces causing rotation of the slave shaft of the device.
The fault of such technical solution is that the inertial transmission transfers rotation in one direction only, that decreases use of all useful work of the inertial mechanism and respectively efficiency factor of the device and its effectiveness in whole. Moreover, the device requires additional energy costs for pump operation.
Besides that, use of mercury (having large specific gravity) as eccentric weight results in increased environmental hazards of such device, because, as it is known, mercury belongs to the 1st hazard class, it evaporates easily even at low temperatures, its vapors and compounds are highly toxic.
The most close to the claimed device is the power drive for rotation, in particular, of the electro generator which action is based on using of intermittent motion mechanism containing a working unit, rotatable, to which alternating rotation moment, generated by the source of mechanical oscillations, is applied (patent RU No. 2377458, 2009).
A centrifugal vibrator in the form of an element of unbalanced mass which is rotated freely by motor and is mounted axially to working unit with preset frequency is used as a source of mechanical oscillations. In this case, the motor and the element of unbalanced mass is mounted on the working unit, and an overrunning clutch is used in the intermittent motion mechanism.
In this power drive centrifugal force of inertia of rotating elements of unbalanced mass (eccentric weight) is used as a source of additional power on its output power delivery shaft.
Defects of such technical solution are as follows:
The purpose of the proposed technical solution is to increase the efficiency factor of the device, its efficiency and reliability, at simultaneous expansion of technical capabilities by simplifying the kinematic scheme of the device and reduction or eliminating of energy losses to overcome the forces of friction in its structural units and consequently, the possibility to generate energy, power of which is much greater than the power of a master motor.
In order to achieve this purpose in the device containing housing in which rotatable drive shaft is installed; master unit, including drive shaft's mechanism of rotation transfer via master wheel, rigidly mounted on the drive shaft, to elements of unbalanced mass, made in the form of wheels provided with additional loads; kinematic chain between master unit and end consumer including working nodes allowing transmission of operating moment according to the claimed technical solution, shaft's rotation transmission mechanism contains not less than two slave eccentric wheels kinematically connected with master wheel, each of which is fixed rotatable on additional immovable slave axles located in parallel with the drive shaft's axle and on both its ends rigidly connected between themselves with connecting element, the balance beam, Which centre is fixed freely on the drive shaft, at this each slave axle is provided with additional connecting link which one end is fixed on the axle and its opposite end is connected with movable element of the working chamber with variable volume including inlet valves for the injecting working medium and outlet valves connected via receiver with end consumer.
Thus, in the claimed design:
Thus, in the claimed structure energy of mechanical oscillations occurring under influence of centrifugal forces of the rotating eccentric bodies (wheels) to which radial acceleration from master motor via drive shaft is imparted, doesn't transform into rotation energy with losses, but transfers directly to working node of the device, and via connecting unit to chambers with variable volumes where mechanical energy transforms into energy of compressed media ready for consumer's use without any additional transformations. The energy of the compressed media received in such a way significantly exceeds in capacity the energy expended for rotation of the drive shaft of the device, which in turn significantly increases the efficiency factor of the latter.
Due to the absence of direct and inverse mechanical connection between the master motor (drive shaft) and working chambers with variable volume, energy consumed by the device is expended solely for achieving by the drive shaft preset rotation speed at which centrifugal forces from the interaction of uniformly accelerated eccentric bodies occur, i.e. to overcome their start inertia and frictional forces in the bearings. As a result, the efficiency factor of the device substantially increases as a whole and its efficiency.
The balance beam with equal shoulders ensures constant kinematic linkage of the master and slave eccentric wheels and limits motion of the loads with which eccentric bodies are provided along the arc relatively to axis of rotation of the drive shaft, which radius is equal to distance between drive shaft and slave axes. The balance beam allows to transfer efforts of eccentric bodies (useful work) only in direction of said arc, being equivalent to both ends of the preset range of motion. I.e. with help of the balance beam the useful work is effected sequentially in the chambers with variable volume, located diagonally. Thus each direction (up down) of the efforts transferred from eccentric bodies to the balance beam is working in the claimed device.
In the offered kinematic scheme consisting of the balance beam and eccentric bodies, useful work at achieved working revolutions of the latter is carried out solely at the expense of the internal forces of the resulted closed-loop system. And as rotating eccentric bodies don't have back kinematic linkage with drive shaft and carry out useful work on the slave axes, not connected with the device's housing, such kind of motion is an unsupported motion not requiring additional power consumption.
Presence of the balance beam allows the entire scheme of the device to be self-balanced in relation to the drive shaft axis at any current moment of its operation in response to the stable balanced eccentric wheels on two slave axes and also diagonally balanced chambers with variable volume.
As in the claimed device motion of the loads has got several degrees of freedom alone the circumference of eccentric bodies and along said arc predetermined by the balance beam motion (adjustable motions of phases, 180° throw-over) and diagonally working chambers with variable volume, it results in smooth operation of the device and the total exclusion of idle moves, which in turn, increases the efficiency factor of the device.
Radial rails of different claimed configurations, with which eccentric wheels can be provided and inside which load is located, ensure additional (along with eccentric wheel motion along the circumference and along said arc predetermined by the balance beam motion) radial movement of the load along the rail under influence of the local drive devices.
And as a result it will ensure dynamic change of the eccentric body centre position—distance from the axis of rotation when rotation speed increases and approximation to it when rotation speed decreases.
It will allow at unchangeable revolutions of the master wheel to change the balance beam's deflection angle in dynamics, which in turn will allow not stopping the entire device's operation to adjust smoothly its power, stroke range of the movable element in the chamber with variable volume and, respectively, quantity indices of the produced working medium. It increases the efficiency factor of the device and improves the working environment.
Possibility to install in the claimed device several slave wheels kinematically linked with the same master wheel on the relevant parallel slave axes and rigidly fixed subsequently on the same balance beam respectively will allow to use several working couples of chambers with variable volume linked by connecting units with each of the slave axes where eccentric bodies are located. Which in turn will allow to generate in the same device energy with variable pressure and consumption of working medium in every subsequent working chamber. It respectively increases technical capabilities of the device and its efficiency.
Thus, said features of the device are essential and sufficient to achieve the objective of the invention.
The principle of operation of the claimed device is explained by the following graphic images, showing the version of the device in which:
In the images are shown:
FIG. 1—scheme of the device (front view), the front housing cover is removed;
FIG. 2—scheme of the device (side view);
FIG. 3—scheme of the device (topside view);
FIG. 4—section A-A of
FIG. 5—general view of the device (axonometric);
FIG. 6—scheme of distribution of mechanical efforts during operation.
The claimed device contains housing 1, wherein drive shaft 2 is installed on bearings. On shaft 2 master gear 3 is fixed with which two slave eccentric gears 4.1 and 4.2 with loads 5.1 and 5.2 respectively. Gears 4.1 and 4.2 are installed on bearings on slave axes, respectively, 6.1 and 6.2 located in parallel to drive shaft 2, fixed rigidly on both sides of the ends of the balance beam 7. Centre of balance beam 7 is fixed freely on bearings on shaft 2. On slave axes 6.1 and 6.2 connecting units respectively 8.1 and 8.2 are installed, each of which in this version is connected by their opposite ends with movable elements of one of the chambers with variable volume, respectively, 9.1 and 9.2, and of oppositely located chambers with variable volume, respectively, 10.1 and 10.2.
In this version the device contains additional analogical master gear 11 and connected with it two slave eccentric gears 12.1 and 12.2, analogically fixed, respectively on drive shaft 2 and on slave axes 6.1 and 6.2 on the side opposite to connecting units respectively 8.1 and 8.2.
In order to avoid unwanted possible occurring unbalanced vibrations during operation of the device at different operating speeds of the drive shaft, the technical solution with four chambers (two cameras per eccentric body) with a variable volume is preferred.
The claimed device operates as follows.
Master power source, such as an electric motor, internal combustion engine, a wind generator, hydro-generator, etc., effort is fed to the drive shaft 2, which is accelerated to a predetermined rotational speed, and drives the master gear 3. In turn, gear 3 drives two slave eccentric gears 4.1 and 4.2, which are free to rotate on bearings fixed in relation to the slave axes, respectively, 6.1 and 6.2.
Gear ratio 1:1 of toothed wheels (master and slave, in case, when they all have identical diameters) provides equivalent cyclical spatial location of the eccentric bodies during each of their complete revolution with respect to their axes of rotation. In case of need to change the gear ratio, subject to an equivalent synchronization of the eccentric wheels, slave and master toothed wheels are made with different diameters calculated for the analogical effort transmission with a calculated necessary distortion (more less) of gear ratio.
Upon rotation of loads 5.1 and 5.2, they are subjected to a centrifugal force of inertia, under the influence of which increases the force of eccentric bodies 4.1 and 4.2 on slave axes, respectively, 6.1 and 6.2, and the balance beam 7 starts reciprocate deviate from its initial position.
Due to the cyclical change in direction of the centrifugal force balance beam 7, synchronously with eccentric bodies 4.1 and 4.2 makes oscillatory motion. The oscillation amplitude is always given and is equal to 2 distances to the points of the extreme positions of the center of mass of loads 5.1 and 5.2, which are determined by calculation.
Efforts of eccentric bodies 4.1 and 4.2, when the balance beam achieves extreme point of deviation, are transferred instantly, i.e. the moment value relatively to the drive shaft is constant. Only their direction changes for 180 degrees at the balance beam's extreme point of deviation when centrifugal force of the loads maximally coincides with the direction of the balance beam, i.e. phase changes smoothly, allowing to take useful effort effectively in both directions.
Through the kinematic chain “Balance beam 7—slave axes 6.1 and 6.2—the connecting units 8.1 and 8.2—movable elements of the chambers with variable volume 9.1, 9.2, 10.1, 10.2” any direction of the oscillation motion of the balance beam drives the movable elements of all chambers with variable volume. In this case, processes of working medium compression in two diagonally opposite chambers 9.1 and 10.2 at balance beam's clockwise deviation and filling processes of the working medium in two diagonally opposite chamber 10.1 and 9.2—at balance beam's counterclockwise deviation occur simultaneously. I.e. any direction of the oscillation motion of balance beam 7 is working, when useful work is effected subsequently in all couples of chambers with variable volume.
Working medium compressed excessively passes to end consumer through exhaust valves (are not shown in schemes) of the chambers with variable volume. As the working medium liquid, gas, air, depending on the set output operating parameters of the claimed devices and conditions (including environmental conditions) of operation may be used.
Exhaust valves of the working chambers may be connected with end consumer through the receiver, in which the energy of the compressed medium can be lossless (in contrast to electrical energy) accumulated for a long time, stored and transported, if necessary, over long distances without use of additional communications in the form, for example, of electric power transmission lines. In addition, it can be used, including, in case of the required increase in power consumption by end consumer of the claimed device. This makes it more efficient in comparison with known devices.
An additional advantage of the claimed structure is its capability to perform an additional function, namely, to create and maintain vacuum in various processing devices, systems and facilities and pump the air and steam-gas mixtures in reservoirs, creating vacuum therein. Moreover, it does not require additional structural transformations, it is enough to swap the functions of input and exhaust valves of the chambers with variable volume. Thus, each of them will operate in the “reverse direction”. With the claimed device medium vacuuming process will also become simple and economical. The presence of such additional function of the device extends its technical capabilities and makes it universal.
Scheme of force distribution during operation of the claimed device is shown in
As a result of operation of drive motor of capacity of 2.2 kW, angle velocity of 298.8 s−1 (2850 RPM) is transmitted to drive shaft 2. At this time master gear 3 which is rigidly fixed on the shaft rotates with the same speed. Since, the gear ratio of each of the master and slave gears is 1:1. (in the illustrated example it is assumed that the diameters of the master and slave gears are equal to each other), the angular velocity of rotation of the slave gears ω, on which loads 5.1 and 5.2 are fixed, is 298.8 s−1, too. The rotation of the eccentric bodies (slave gears) creates a centrifugal force of value:
F
c
=m·ω
2
·r=8570 N,
where:
Radial component Fx of the centrifugal force Fc doesn't affect operation of the device because it is balanced by similar force created by symmetrically located second eccentric body. Instantaneous value of the tangential (to the path of radius R) and radial simultaneously—to the path of radius r, component of centrifugal force Fc is a force F, which is applied along line S to axis of the eccentric and from there—to the chamber with variable volume, and is equal to:
F=2·m·ω2·r·cos ωt,
where:
F=8570 N
V=ω·r·cos ωt
And at t=0: V=9 m/s
Thus, the angular rotation velocity Ω of the master gear around Z axis is significantly less than the angular velocity ω, therefore, it may be neglected.
M=F·R,
where R—distance from axis Z to loads rotation axes, m, then:
M=8570·0.14=1200 Nm.
P=M·ω
b np ωb=φ/t,
where:
ωb=0.42/0.02=21 rad/s,
P=1200·21=25200 (Wt)=25.2 kW.
Wherefrom it follows that the theoretical capacity of the balance beam (25.2 kW) more than 10 times exceeds the initial motor capacity (2.2 kW), rotating drive shaft.
In the claimed device size and weight of the eccentric bodies is designed so that the balance beam 7 deviates by a predetermined value at rated speed of drive shaft 2, carrying out oscillating movements with a predetermined amplitude and via connecting units 8.1 and 8.2 transmits efforts of eccentric bodies equal to the force F to the chambers with variable volume. While movable elements in chambers with variable volume move for the distance equal to given amplitude of balance beam's oscillations 7.
I.e. in the claimed device, only the force F is used to generate in the chambers with variable volume of compressed working medium with high (excessive) pressure. Thus, drive motor energy, consuming by the device directly to increase pressure of working medium in chambers, doesn't. increase.
Moreover, as above calculations shown, the energy, generated by the claimed device and transmitted to the end consumer of compressed medium, numerously (more than 10 times) exceeds the capacity of motor spent for the drive of the device, which indicates the high efficiency factor of the device as a whole.
Comparative estimate characteristics of efforts (loading) distribution during operation of the claimed device and of one of the known devices for producing (generating) an energy source in the form of a compressed medium (air), in particular a reciprocating compressor, are shown below.
Calculations Are Performed for the Following Example of Compared Devices:
Here it Is Assumed that in Compared Devices:
F
response
=P·S=5.0 kN:
Fresistance=0.3 kN;
F
response
=P·S=5.0 kN;
Fresistance=0.3 kN.
F=2·(Fresponse+Fresistance)=10.6 kN.
Since in the claimed scheme there is no direct kinematic connection between the drive motor and piston group, the calculation of the motor capacity is made as follows. We estimate the required motor capacity designated for rotation of loads, provided that their efforts will produce the estimated useful action of 10.6 kN at angular velocity 2850 RPM.
In the established (running) mode drive motor capacity is spent only to overcome friction in the bearings and in gears.
C
L=1.047·10−3·Mfr·n, npH Mfr=0.5·k·Fb·d,
where:
M
fr=0.5·0.001·2650·2.5≈3.3 N·sm,
and capacity losses in one bearing:
C
L=1.047·10−3·3.3·2850≈12.0 Wt.
Thus, the claimed technical solution allows receiving, accumulating, storage, transportation (in particular, in sealed containers) and carrying for any distance of cheap, environmentally friendly energy source - compressed medium. The cost of production (generation) of the energy source is reduced by several times without loss of volume due to the saving of any energy consumed by the device in whole.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2011 13627 | Nov 2011 | UA | national |
| Filing Document | Filing Date | Country | Kind | 371c Date |
|---|---|---|---|---|
| PCT/UA2011/000122 | 12/2/2011 | WO | 00 | 5/13/2014 |
