WO2009003261A2

WO2009003261A2 - Electrodynamic rotary closed-circuit machine

Info

Publication number: WO2009003261A2
Application number: PCT/BY2008/000005
Authority: WO
Inventors: Anatolij Semenovich Berjukov
Original assignee: Zakrytoje Aktsionernoje Obschestvo 'alsan-Bi'; Zakrytoje Aktsionernoje Obschestvo 'termeks'; Britson Trade Inc.
Priority date: 2007-07-04
Filing date: 2008-07-02
Publication date: 2009-01-08
Also published as: WO2009003261A3

Abstract

The invention relates to mechanical engineering and can be used for power supply to high-power devices, for example ship propeller shafts, industrial electric generators and the similar technical devices. The inventive electrodynamic rotary machine comprises a closed hydraulic circuit with a pump and a rotary engine. Decompression chambers are made on the cylindrical surface of the engine rotor. The cross-section of the decompression chambers is in the form of truncated cones with an apex angle α = (19-22)°. The base of the cone is conjugated with an input channel. A distance between the small and large bases of the cone of the chamberis not less than 14-16% of the length of the input channels. Output channels connected to an annular gravitation chamber are made in the body. Four segments are secured inside the body in such a way that they are displaceable in one way by means of an adjusting screw. The input channels are coupled to hydraulic storage collectors and the output channels are coupled to a circulating tank. Said tank is coupled by means of pumps to the storage collectors. The pipeline of the storage-collectors is provided with a distribution manifold which is linked to compensating accumulators and is connected to the pump. The rotor shaft is connected to an electric power generator. Said invention makes it possible to improve the power and operational parameters of an electrodynamic rotary machine.

Description

5 ELECTROHYDRODYNAMIC ROTARY

CLOSED CYCLE MACHINE

Application area.

The invention relates to the field of engineering, energy, shipbuilding and is intended for the power supply of high

JO power, for example, ship propeller shafts, industrial power generators and other similar objects of technology. The prior art.

A known method and device for converting energy into mechanical energy of rotation of the rotor (1). The working body is placed in a closed

12th cavity of the rotor, covering its axis of rotation, the walls of which have at least one curved surface formed by a segment of a curved line. An annular cavity is used to accommodate the working fluid. As a working fluid, in particular, high density liquid is used. The rotor cavity communicates with the source

20 hydrostatic pressure and with a cooling system of power and technological installations, as well as with an energy source using a camera covering the rotor shaft and designed to accommodate the energy carrier. A rotor with a working fluid cavity is placed inside a hollow and sealed housing connected to a source of _j g of energy, and the energy carrier is passed through the housing cavity into the rotor cavity through the end walls of the rotor, while the cavity in the rotor is used as a heat exchanger for cooling energy, technological and refrigeration systems installations. As a curved line for the formation of the cavity of the rotor, use a spiral of Archimedes, _o about or the involute of a circle (circle), or an ellipse, or a parabola, or perbola, or cardioid. The rotor cavity is communicated with a heat generator, while the rotor is installed in the housing using a rotation unit and is provided with a cavity for the working fluid, which is closed, covering the axis of rotation and having at least one curved surface from a section of one of the above curves lines.

The rotor cavity is communicated with the energy source using a heat pipe. The heat pipe is placed in the rotor shaft or in the end wall of the rotor cavity, while the rotor cavity is connected to the feed chamber of the working fluid and the chamber of the removal of the working fluid from the rotor cavity by channels in the rotor shaft, and the housing wall is provided with a cavity designed to accommodate the energy carrier. The chamber for accommodating the energy carrier has channels for supplying and discharging the energy carrier, while the rotor with the working medium cavity is installed in the rotor of the mechanism coaxially with this rotor and is rigidly fixed on it and equipped with a heat generator, and internal energy is supplied to the working medium in the rotor cavity by water supply from a reservoir to a device by gravity or by force.

A disadvantage of the known technical solution is the use of an open system for supplying a working medium and a low-efficient heat exchange system between the rotor and the housing, which reduces the efficiency of the device.

A rotary hydraulic machine with axial inlet and peripheral outlet pipes (2) is proposed. The machine contains a housing, a working body in the form of a rotor with hydraulic channels and connected to the drive shaft. The rotor is made in the form of bodies of revolution, for example a hemisphere or a truncated cone with a receiving chamber in a narrow part of the rotor. Inside the rotor volume, hydraulic channels are made in the form of multi-helical branching and diverging spirals from the chamber to the periphery. The outputs of the channels are located either at the periphery in the wide part of the rotor or at its end. The hydraulic channels in the section have a round or any other shape, and the spiral screws made at an angle ^ = n, where n> 0 with a given step from 0.5 to 1 of the height of the rotor along its axis, and the receiving chamber is made in the form of a truncated cone.

The disadvantage of such a rotary machine is the technologically difficult hydraulic channels of the rotor, as well as the insufficiently efficient conversion of the kinetic energy of the working medium into the mechanical energy of rotation of the rotor.

Patent (3) describes a rotary hydraulic motor containing an external thermal energy source, working chambers that are fixed relative to the axis of the working shaft and filled with a liquid working fluid with continuously varying volumes during a revolution of the working shaft. The mechanism for converting the expansion energy of the liquid working fluid into the mechanical rotational energy of the working shaft and the switchgear provides the filling phases when the working chambers are connected to the supply line and the displacement phase in which the working chambers are connected to the drain line, as well as the intermediate phases in which the working chambers have minimal volumes and are disconnected from both highways. The liquid working fluid has a thermal volume expansion coefficient greater than that of the walls of the working chambers. Supply line, drain line, refrigerator, safety valves and pipelines connecting the working chambers through the safety valves with the drain line. According to the invention, the distribution device provides the phases of volumetric thermal expansion, in which the conversion of thermal energy into mechanical energy occurs, the refrigerator is included in the hydraulic connection of the supply and drain lines, and external thermal energy is constantly supplied to the working chambers. The working chambers are located around a circle with the possibility of circular motion, consistent with the rotation of the working shaft, and external thermal energy is supplied to the working chambers in the phase of thermal volume expansion.

The disadvantage of such a hydraulic motor is the low coefficient of conversion of thermal energy into rotational energy and, as a consequence, the low economic efficiency of the engine.

Patent application (4) proposes a rotary engine with pistons rotating in the rotor chambers, which are made in the shape of a four-pointed star. The working fluid is supplied under pressure to the rotor chambers and ensures its rotation. Also known is a rotary hydraulic motor with oscillating inertial pistons (5). The engine rotor contains at least four oscillating inertial pistons mounted on the pivots, preferably on a floating bearing. Between the rotor and the motor casing, an annular gravitational chamber is made, separated from the rotor by an assembly sleeve, which consists of at least four segments attached to the motor casing. Each segment of the sleeve of the gravitational chamber preferably ends at one end with an inlet and at the other end with a double outlet, creating a labyrinth seal at the junction of two adjacent segments. The engine housing also contains two pairs of control windows, one pair of windows is located in the idle zone of the inertial piston, and the second pair of windows is in the working area of the inertial piston. Each inertial piston is provided with a channel for lubricating the piston bearing. The gravity chamber is configured to adjust its volume by means of an adjusting screw.

A disadvantage of the known technical solutions is the technological complexity of the manufacture of the rotor and the low operational reliability of such structures as a whole. The closest in design to the offer- To the invention, a pulsed gravitational inertial closed-loop engine, which was chosen as a prototype (6). The engine comprises a housing with a rotor located therein. On the outer cylindrical surface of the rotor, decompression chambers are made in an amount of at least four. Each pair of chambers is configured to periodically communicate with the intake and exhaust channels of the working fluid. High-pressure channels are placed in the engine housing perpendicular to the outer generatrix of the cylindrical surface of the rotor and are connected to the intake chambers, which are made in the form of a truncated cone of ellipsoidal shape. The decompression chambers in cross section are made in the form of an ellipse, with the ratio of the diameter of the rotor D _po. to the diameter of the decompression chamber d _dk selected from the calculation: D _po .> 9d _dk . The length of the inlet channel is not more than 85% of the stroke length of the decompression chamber in the duty cycle along the outer forming cylindrical surface of the rotor. The total volume of the compression chambers together with the volume of the intake channels in the phase of the working cycle will be no more than 95% of the maximum volume of the working fluid pumped in the phase of the working cycle to provide an engine drive. The magnitude of the angular displacement of the decompression chamber in the working phase for one revolution of the rotor is (72 ± 2) °, and the magnitude of its angular displacement in the dead zone is (20 ± 2) °.

A gravitational chamber is placed in the engine casing, formed between the inner cylindrical surface of the casing and a special shell in the form of a sleeve mounted on the inner cylindrical surface of the casing with the possibility of tight fit to the cylindrical surface of the rotor. The sleeve is made by a team of four segments, which are mounted by means of fixing bolts with spacer sleeves, providing the formation of the specified cylindrical cavity. Each hub segment is equipped with a calibration hole with an adjusting bolt to provide one-way him moving the segment. The magnitude of the indicated displacement is set by the adjusting bolt. The ends of the segments are provided with grooves with the possibility of forming labyrinth seals at the joints.

Bearing assemblies are mounted in the housing and the cover, on which the rotor output shaft is mounted. Bearing units are closed by front and rear covers. The rotor shaft, as well as the covers, are equipped with sealing glands to prevent leakage of the working fluid - hydraulic oil. The motor housing at the base contains holes for mounting to a foundation or a supporting frame. The engine is driven from an external closed hydraulic circuit by a hydraulic pump by supplying a working medium under pressure - industrial oil through high pressure channels into the decompression chambers of the rotor. Oil under a pressure of about 65 MPa is pumped into the high-pressure channel and then through two inlet channels located in front of the working zone, tangentially, in opposite directions directed by jets, is injected simultaneously into decompression chambers opposite to the rotor. As a result of the sharp expansion, the hydrostatic compression energy of the working medium is converted in the decompression chamber to the kinetic rotational energy of the working medium flow, which rotates the rotor and creates a torque on the motor shaft. At the same time, two other decompression chambers placed on the rotor at the same time are located in the “dead” idle zone of the working cycle and, as the rotor rotates, communicate with the chamber and the exhaust channel, due to which the used oil from these chambers is discharged and the cycle repeats. For one revolution of the rotor, two cycles take place: the working stroke, where oil is injected into one pair of decompression chambers and the “dead” cycle (idle), where waste oil is removed from the other pair of decompression chambers through the exhaust channel. The disadvantage of the prototype is the low degree of conversion of the energy of the hydrostatic pressure of the working medium into the mechanical energy of rotation of the rotor, which is due to structural disadvantages of the geometric shape of the decompression chambers of the rotor and leads to a decrease in the efficiency of the device as a whole.

The objective of the invention is to remedy these disadvantages and improve the technical characteristics of the device.

The technical result is to increase the energy and operational parameters of an electrohydrodynamic rotary machine. SUMMARY OF THE INVENTION

The problem is solved in that the electrohydrodynamic rotary machine is a closed cycle, containing a closed hydraulic circuit with a pump, a rotary motor, in the housing of which a shaft with a rotor is mounted, on the outer cylindrical surface of which at least four decompression chambers with intake channels are made, as well as exhaust channels made in the housing and connected with an annular gravitational chamber placed around the rotor between the housing and the prefabricated annular shell in the form of at least four seconds The segments are mounted on the inner cylindrical surface of the housing with the possibility of their one-sided movement by means of adjusting screws passed through the calibration holes made in the segments connecting the gravity chamber with the intake and exhaust channels according to the invention, and the rotor decompression chambers in the cross section are made in the form of truncated cones with an angle at the apex in the range α = 19 - 22, while the smaller base of the cone of the chamber is conjugated with the inlet channel, and the distance d between the smaller and the pain the bottom of the chamber cone is at least 14 - 16% of the length of the inlet channels, the last They are functionally connected with hydraulic accumulators, and the outlet channels are connected via pipelines through the exhaust manifold to a circulation tank, which is connected by a system of pipelines with coarse and fine filters through high-pressure pumps with an autonomous electric drive, and the pipeline of the latter is equipped with bypass valves and a manifold - distributor, which is connected with hydraulic accumulators-compensators It is connected to a manual hydraulic pump a high-pressure, and the rotor shaft is connected via a clutch to the electric generator which is connected to the external electricity distribution network to the load through the voltage regulator.

The invention is illustrated by drawings in Fig.1 - 4.

FIG. 1 is a schematic diagram of a closed loop electrohydrodynamic rotor machine.

Figure 2 is a General view of the engine in cross section.

In Fig. 3 is a cross-sectional view of a rotor decompression chamber.

Figure 4 is a vector diagram of the decomposition of the forces of the hydraulic fluid flow in the decompression chamber of the rotor.

The electrohydrodynamic rotary machine 1 contains a rotary engine 2, which is functionally connected to a closed hydraulic circuit 3, an electric generator 4 and an external distribution electric network 5. The rotary engine 2 includes a housing 6 with an output shaft 7 and a rotor 8 mounted on it, on an external cylindrical of the surface .9 of which at least four decompression chambers 10 with inlet channels 11 are made. Each decompression chamber 10 is made in the form of a truncated cone with a distance between large and smaller bases d = (14 - 16)% of the length of the inlet channel 11 and with an angle at the apex of the cone α = (19 - 22) °. The smaller base “C” of the cone of the chamber 10 is associated with the inlet channel 11. The larger base of the cone is made curved with a radius of curvature r = Vi D, D is the diameter of the lower base of the cone. In the housing 6 around the rotor 8 is placed an annular gravity chamber 12 formed by a prefabricated annular shell 13, consisting of four segments 14, mounted on the inner cylindrical surface 15 of the housing 6 with fixing screws 16 with spacer sleeves 17. The segments 14 contain the missing adjustment screws 18 through calibration and adjustment holes 19 connecting the gravity chamber 12 with the intake channels 11. The segments 14 at the ends contain grooves 20 and 21, which together form a labyrinth seal 22.

An exhaust channel 23 is made in the housing 6 of the engine 2 with an exhaust chamber 24 connected to a closed hydraulic circuit 3 through a low pressure channel 25 with a distribution manifold 26 through a drain pipe system 27 with a circulation tank 28. The high pressure channel (not shown) the housing 6 of the engine 2 by a system of high pressure pipelines 29 of the hydraulic circuit 3, through the distribution manifold 30 by a pipe 51 connected to the storage batteries 31, the distribution manifold 32, pulse accumulators compensator 33 and high pressure pumps 34 through pipelines 48 provided with bypass valves 35. The closed hydraulic circuit 3 also includes a starter battery 36 for starting the start pump 47, connected to the pipe 50 and a backup high pressure pump 37 for manual emergency start, return system pipelines 38 with coarse filters 39, pipelines 40 with fine filters 41, high pressure hydraulic pumps 34.

An electric generator 4 is connected to the output shaft 7 of the engine 2 through an elastic coupling 46 and connected to an external distribution network 5 through a voltage regulator (PH) 42, which The first one is electrically connected to the main switchboard (main switchboard) 43, the secondary consumer disconnection switchboard (SHOVP) 44 and the closed-circuit load distribution switchboard (SHRN) 45. Implementation of the invention.

Electrohydrodynamic rotary machine closed loop 1 operates as follows. Fill the circulation tank 28 of the closed hydraulic circuit 3 with a working fluid-hydraulic medium, for example, industrial oil. The starting battery 36 starts the starting pump 47 and the oil from the circulation tank 28 through the return pipe system 38 with coarse filters 39 through fine filters 41, the pipe 40 and the distribution manifold 32 with a bypass valve 35 are supplied to the pulse compensation batteries 33 and to the batteries- drives 31 until operating pressure of 25MPa is reached. The operating pressure is regulated by the bypass valve 35, and the excess oil through the return pipe (not shown) is discharged into the circulation tank 28. During compression in the storage batteries 31, the oil is heated to a temperature of about 95 ⁰ C. Further, from the compensator batteries 33 and storage batteries 31 through a distribution manifold 30 with flow controllers and speed controllers for the high pressure piping system 29 hot oil through high pressure channels (not shown) in the housing all 6 in the duty cycle of the engine 2 is fed into the gravity chamber 12. From the chamber 12 through the calibration and adjustment holes 19 under a pressure of about 25 MPa, oil is injected through the inlet channels 11 into two decompression chambers 10, opposite placed on the rotor 8. When passing through calibration and adjustment holes 19, which have a special shape (not shown in the drawing) and inlet channels 11, vortex structures are formed in the oil flow, which in the decompression chamber 10 decompose with a sharp expansion and cooling to a temperature of the order of (-5 ...- 7) ° C with simultaneous braking, accompanied by the transfer of the energy of the vortex flow of the working medium to the kinetic energy of rotation of the rotor 8 and creating a torque on the output shaft 7 At idle (in the “dead” cycle) of rotor 8, used oil from decompression chambers 10 through the exhaust channel 23 through the exhaust chambers 24 through the low pressure channel 25 in the housing 6 and further through the low pressure drain piping system 27 with a distribution manifold 26 laminas The flow stream is discharged into the circulation tank 28. Then, the oil from the circulation tank 28 is pumped through the return piping 38 through the coarse filters 39, fine filters 41 and returned to the compensator-accumulators 33 and accumulator-accumulators 31 for reuse in the system closed cycle electrohydrodynamic rotary machine 1.

When oil is supplied to the annular gravity chamber 12 due to pressure, the segments 14 constantly compress the cylindrical surface of the rotor 8 due to the possibility of shifting one end of the segment 14 in the radial direction along the adjusting screw 18 and due to the movable design of the mechanical labyrinth seal 22 grooves 20 and 21. Calibration and adjustment the holes 19 are made in a special shape (not shown in the drawing) and together with the inlet channels 11 provide the formation of a vortex flow of the working medium in decompression chambers 10. Forms and decompression chamber 10 in the form of a truncated cone, as well as the ratio between the larger and smaller bases of the cone d = 14 - 16% of the length of the inlet channel 11, at a selected angle at the apex of the cone α = (19 - 22) °, provide an optimal energy exchange mode between the working medium and the rotor 8 of the engine 2. The latter is also provided by the design the interface elements of the smaller base “C” of the cone of the decompression chamber 10 with the inlet channel 11, it being essential that the larger base of the cone “D” is made curved with a radius of curvature r = VT. D, D - diameter of the lower base of the cone. This design guarantees the elimination of the development of reverse hydraulic shock in the stream when oil is admitted to the decompression chamber 10 and, as a result, braking of the rotor 8 with loss of power on the shaft 7, while the gravitational chamber 12 compensates for the effect of anti-gravity “flooding” of the rotor 8 at high rotational speeds, which also reduces engine power loss 2.

Through an elastic coupling 46, the torque from the output shaft 7 of the rotor 8 is transmitted to the shaft of an alternating or direct current electric generator 4, which ensures the generation of electric energy and its supply through the voltage regulator 42 to an external distribution electric network 5. After applying electric current to the load distribution board In a closed cycle ЩРН 45, the main hydraulic pumps 34 are turned on, the starting hydraulic pump 47 is turned off automatically. After the generator 4 reaches the operating mode, external consumers of electrical energy are connected through the main switchboard of the main switchboard 43. The off-board of secondary consumers SHCHOVP 44 serves to disconnect external secondary consumers of electric energy from the external distribution electric network 5 in case of overload of engine 2 over 25% of rated power.

From the prior art it follows that the claimed technical has novelty, which is expressed in the design of the decompression chamber 10 of the rotor 6 in cross section in the form of a truncated cone with fundamentally new parameters: the angle at the apex in the range of α = 19 - 22 °, at this smaller base cone chamber mates wife with an inlet channel 11, and the distance between the smaller and larger bases of the cone is not less than 14 - 16% of the length of the inlet channel 11. This design decompression chamber 10 provide, in comparison with the prototype, the creation of a very effective vortex flow of a liquid working medium when it is injected through the inlet channel 11 into the cavity of the decompression chamber 10. Studies have shown that in a stream of liquid supplied under a pressure of about 25 MPa to the decompression chamber 10, with the selected design parameters of the rotor 8, it forms I have a well-defined type of vortex motion. With the subsequent sharp drop in the liquid pressure in the chamber 10 due to expansion, its temperature drops rapidly, and the released thermal energy is converted into kinetic energy of rotation of the jet, which makes an additional contribution to the mechanical energy of rotation of the rotor 6. The technical solution has an inventive step, since from the previous level it is not obvious to the technician that with the declared parameters of the device, the nature of the turbulent energy exchange between the liquid working medium and the rotor 6 increases the energy ordered vortex motion due to a decrease in the energy of chaotic thermal motion of the molecules of the working medium, i.e. by reducing the temperature of the oil in the decompression chamber of the rotor 8. The linear speed v of the vortex rotation of the liquid jet working medium, which is thus added can be estimated from the expression: y - c _p Δ T = v ^2/2,

where η is the efficiency of turbulent conversion of thermal energy into kinetic energy;

C _p - specific heat of industrial oil (2.1 kJ / kg- ° C). Assuming that η = 0.5 due to a decrease in the oil temperature Δ T by 95 ⁰ C, a linear velocity of about 7 m / s is additionally reported to the working medium. Thus, as a result of a decrease in temperature, which accompanies the twisting of the mass flow of liquid

5 of the medium in the decompression chamber 10, the pressure in the so-called "pressure valley" drops even more and, accordingly, the central forces of the pressure gradients increase. This leads to more efficient twisting, i.e. the vortex self-acceleration mode is activated. With the further development of the vortex flow process, self-acceleration of

It is smeared due to the fact that, as the linear velocities of the swirling liquid jets increase, centrifugal forces and turbulent friction forces begin to play an increasingly important role. In the stationary mode, when for each element of the rotating masses of fluid the centrifugal force balances the vector sum of the forces of the baric gradient and

15 of turbulent friction, the trajectories of fluid flows are converted into spirals converging to the center. The selected angle range in the range α = 19–22 ° at the apex of the cone of the decompression chamber 10 corresponds to the fundamental value of the electron anisotropy angle equal to ~ 22 °. Such parameters of the decompression chamber provides

The additional stability of the formed vortex structures due to their energetic feed from the environment by activating the working medium during its interaction with the electron-positron component of the physical vacuum (7).

r _{y s} Fig. 4 is a vector diagram of the decomposition of the forces of the hydraulic fluid of the working fluid in the decompression chamber 10 of the rotor 8, where the vectors C and D correspond to the forces acting in the "baric valley", the resultant of which is directed to the center of the vortex flow and provides an effective reduction pressure in

_{O 0 of the} vortex structure, and the vectors A and B correspond to the additional forces acting tangentially and responsible for an additional increase in the linear velocity of rotation of the vortex structure of the liquid working medium. Thus, it is obvious that the additional energy contribution obtained by converting the thermal energy of the liquid working medium into the mechanical energy of rotation of the rotor 8 ensures the achievement of the claimed technical result and the industrial applicability of the invention.

Information sources:

1. RU JNe 96116284 A, 1998.11.20.

2. RU 2005134491 A, 2007.05.20.

3. RU 2295650 C2, 2007.03.20.

4. WO 02/092968 Al, 2002.11.21.

5. WO 2005/068839 Al, 2005.07.28.

6. WO 2005/100778 Al, 2005.10.27. (prototype).

7. About "Theory of the fundamental field" IL Gerlovina, I-ITTP: // PSI-

Claims

Claim

1. An electrohydrodynamic rotary machine of a closed cycle, comprising a closed hydraulic circuit with a pump, a rotary engine, in the housing of which a shaft with a rotor is mounted, on the outer cylindrical surface of which at least four decompression chambers with inlet channels, as well as exhaust channels made in the housing and associated with an annular gravitational chamber placed around the rotor between the housing and the prefabricated annular shell in the form of at least four segments fixed to the inside the cylindrical surface of the housing with the possibility of their one-sided movement by means of adjustment screws passed through calibration holes made in the segments connecting the gravity chamber with the intake and exhaust channels, characterized in that the rotor decompression chambers in cross section are made in the form of truncated cones with an angle at the apex of the interval α = (19 - 22) °, while the smaller base of the cone of the chamber is conjugated with the inlet channel, and the distance d between the smaller and larger bases of the cone of the chamber is accounts for at least (14 - 16)% of the length of the inlet channels, the latter being functionally connected to hydraulic accumulators, and the outlet channels are connected via pipelines through the exhaust manifold to a circulation tank, which is a piping system with coarse and fine filters, high pressure pumps with self-contained electric drive, connected with hydraulic accumulators, and the pipeline of the latter is equipped with bypass valves and a manifold - distributor, cat ing connected with hydraulic accumulators-compensators and is connected to a manual hydraulic pump to the high pressure, and the rotor shaft dviga- The device is connected via a coupling to an electric generator, which is connected to an external distribution electric network with a load through a voltage regulator.