RU2422733C1 - Heat cavitation generator - Google Patents

Abstract

FIELD: power industry. ^ SUBSTANCE: heat cavitation generator includes rotor formed by means of in-series installation of centrifugal and cavitation wheels of semi-open type, guide vanes with vaned grid, suction and delivery covers with brackets of support assemblies. Cavitation wheels are made in the form of perforated conoidal-cylindrical nozzles of disc with radial-beam blades, which are framed in circumferential direction with cylindrical perforated rim, and guide vanes of cavitation stage is provided with perforation in inter-vaned zone. At that, support on cavitation stage is created with conical nozzle head piece which is installed at the outlet of flow of treated medium from vaned diffuser of housing of pre-cavitation stage. ^ EFFECT: increased number of cavitation generation zones and hydraulic impacts on opposite flows of jets which are throttled through conoidal-cylindrical perforation nozzles, which leads to uneven growth of temperature gradient in the stage. ^ 2 cl, 4 dwg

Description

FIELD OF THE INVENTION

The invention relates to alternative forms of energy, in particular, to units designed to create temperature fields in autonomous closed-loop heat supply systems, to heat local stationary facilities, in technological processes that require changes in the rheological properties of the processed media by the temperature effect on them during pumping, in process plants mixing, dispersing, cleaning, as well as hydraulic fracturing of the reservoir in the development of minerals.

State of the art

Thermal generators or devices are known in which hydrodynamic thermal heating methods are generated that are generated in dynamic turbomachines by oscillatory, cavitation or other processes that are formed in a moving fluid, by means of concomitant mechanical action during turbulent mixing of the layers, contact of the flow with the surfaces of the parts of the flow part and the body, throttling through gap and end seals, as well as arising in the system of hydraulic shocks, etc.

In the overall efficiency (hereinafter referred to as efficiency) of dynamic turbomachines, the indicated energy inputs are taken into account by mechanical and hydraulic efficiency and are considered as natural losses associated with the processes of transportation and pumping of liquids.

Cavitation phenomena, which consist in the formation of local regions in a liquid in which vapor-gas caverns are released followed by their destruction, are the result of a fast-moving process of vapor condensation and collapse of bubbles, accompanied by high-frequency hydraulic micromolets and high pressure drops in the local region (see Bashta T.M Hydraulic drives of aircraft. - M.: Mechanical Engineering, 1967. - 497 pp., Ill.).

Cavitation usually occurs in dynamic turbomachines, pipelines, as well as in all devices where the fluid flow sharply changes direction, is exposed to narrowing of the flow path with subsequent expansion - in taps, valves, valves, diaphragms.

Cavitation, violating the established operating mode of hydraulic machines and their systems, leads to the destruction of aggregates, valves and pipelines, most often operating at significant pressures and flows.

It is known that cavitation has a particularly negative effect on the operation of dynamic pumps and turbomachines when, for one reason or another, the unit detaches flow from the working surface of an element that carries out the transportation or movement of the liquid. The possibility of such separation of the flow depends on the magnitude of the pressure of the liquid on the suction path, its rheological properties, as well as the design and technological design and the speed of the pump. For example, cavitation can occur if the pressure at the suction pipe inlet is insufficient to ensure continuity of the fluid flow during a change in its speed, defined by a change in the speed of the suction valve of the pump unit. The maximum permissible number of revolutions of the pump is such a number at which the absolute pressure of the liquid on the suction path will be able to overcome the sum of losses in it without breaking the flow.

In the case of vane and vortex pumps, the losses due to centrifugal force are added to the internal suction losses considered.

With the advent of cavitation, the performance of dynamic turbomachines decreases, characteristic noise occurs, emulsification of the liquid occurs, and sharp frequency fluctuations in pressure in the discharge line and shock loads on the pump parts, which can cause the unit to fail, are observed.

In cavitation zones, destruction (erosion) of hydraulic unit parts occurs with the formation of characteristic damage (in the form of caverns, shells) on their surfaces.

There are several hypotheses about the nature of the phenomenon of cavitation and about the mechanism of its destructive effect on hydraulic units and their elements, the most common of which boils down to the following. When the pressure decreases at any point in the fluid flow to a value lower than the pressure of its saturated vapors at a given temperature, the liquid boils (it ruptures), the released vapor bubbles are entrained by the flow and transferred to the higher pressure region, in which the vapor bubbles condense (close) . Since the process of condensation of a vapor bubble (cavity) occurs instantly, fluid particles filling its cavity move to its center with great speed. Theoretical calculations show that the meeting speeds of the walls of a closing bubble (cavity) can reach values exceeding hundreds of meters per second. As a result, the kinetic energy of the colliding particles of the liquid causes local hydraulic shocks at the moment of condensation completion (at the moment of closing of the bubbles), accompanied by sharp pressure and temperature overflows in the condensation centers. Theoretical calculations show that the local pressure casting with swift (in a time of approximately from 1 ^-3) destruction (closing) of the cavitation bubble may reach 2,000-3,000 kg / cm ^2.

If condensation of vapor bubbles occurs near the wall of the unit body or channel, then it will undergo continuous hydraulic shocks with high repeatability from the side of the liquid particles. As a result, during prolonged cavitation under the influence of the indicated hydraulic shocks and the simultaneous action of high temperature developing in the centers of condensation of these shocks, microscopic shells (depressions) are formed on the wall surface in a short time, the growth of which is associated with the duration of exposure.

The studies showed that the cavitation phenomena observed in practice mainly occur not as a result of the release of liquid vapor, but as a result of the release of dissolved air from the liquid in the zones of low pressure, as well as the expansion of the latter bubbles in a mechanical mixture with the liquid (see Bashta T. M. "Hydraulic drives of aircraft," - M.: Mechanical Engineering, 1967. - 497 pp., Ill., See also T.M.Bashta. "Engineering Hydraulics", M .: Mechanical Engineering, 1971, - 671 c.).

The latter is confirmed by the fact that cavitation does not begin at the vaporization pressure in the liquid, but at a certain critical pressure significantly exceeding the vaporization pressure. Long-term tests of various hydraulic systems also found that in real conditions when operating dynamic turbomachines, it is impossible to create a vacuum that would correspond to the vapor pressure of the fluid. The development of such low pressures (vacuum), corresponding to the vaporization pressure in the liquid, is hindered in this case by air, which is both in the dissolved state and in a mechanical mixture with the liquid in the form of bubbles of one size or another, which instantly expand with any decrease in pressure.

This assumption is also confirmed by the fact that cavitation begins the earlier, the more air is contained in the liquid, while deaerating, its cavitation resistance increases (the beginning of cavitation is shifted to the higher vacuum zone).

Studies allow us to conclude that cavitation and cavitational destruction of the surfaces of parts of hydraulic units occurs as a result of mechanical impact of hydraulic shocks that occur when air cavitations (bubbles) are closed, and also as a result of heating of these surfaces during these shocks to high temperatures.

The mechanism of this phenomenon can be schematically represented in the following form. When air bubbles enter the zone of high pressure, they close at a high speed (collapse), while smaller ones dissolve in the liquid, and larger ones sharply decrease in volume. During the closure of the bubble, the particles of the surrounding liquid move with great speed to the center of the bubble and the kinetic energy of these particles creates local hydraulic shocks with large, instantly (shock) increasing pressure overflows in the center of the bubble.

Due to the high speed and high level of compression of the air bubble, high temperatures develop in it, which, according to calculations, can reach 1000-1500 ° C and above with the adiabatic compression process. Impacts of liquid particles upon the closure of such a bubble on the surface of a part cause its local heating to such a temperature, the combination of which with impacts leads to intense erosive destruction of the material.

The possibility of the separation and participation in the phenomenon under consideration of liquid vapor bubbles, the formation of which will be facilitated by its disturbance during a flow with a large pressure drop, a local sharp increase in temperature, and active air release, is also possible.

Under the influence of these temperatures in the presence of atmospheric oxygen, active oxidation (corrosion) of surfaces occurs. It should also be noted that the oxidation processes that occur in this case are exacerbated by the fact that the air dissolved in a liquid contains more oxygen than atmospheric.

At the same time, the intensity of oxidation processes also increases as a result of the fact that under the influence of mechanical (hydraulic) micro impacts, the oxidation film is destroyed, which under normal conditions protects the metal surfaces of parts from oxygen and slows down their oxidation. Since this film has reduced mechanical properties, it is easily destroyed (crushed) under the influence of hydraulic micro-impacts and is carried away by the stream, exposing unprotected sections of the metal surface.

Observations show that with the appearance of the first ulceration (roughness), the intensity of further cavitation destruction increases sharply. Equally, the process of cavitation destruction is accelerated in the presence of roughnesses, microcracks and other local defects on the surfaces of parts. When cavitation cavities are collapsed in this case, accompanied by high-level and high-pressure hydraulic microflows, high shock pressures arise in the pores (microcracks) that exceed the pressure of the hydraulic shock when the cavity collapses, under the action of which the fluid is forced into the pores, compressing the air in the pores, which heats up to high temperatures.

Obviously, a certain role in enhancing cavitation fracture in the presence of roughness is also played by the fact that the surface roughness increases its area in comparison with the area of the same smooth surface.

Observations also show that cavitation occurs the earlier, the more the liquid is contaminated with solid particles. The latter is due to the fact that a thin layer of air is adsorbed on the surface of polluting solid particles, the particles of which, when they enter the zone of reduced pressure, serve as germinal foci that contribute to the occurrence of cavitation.

The first designs of hydrodynamic heat generators based on cavitation processes appeared in the early 70 ... 80s and were used to generate thermal fields:

- laboratory and technological installations, including methods for reproducing in laboratory conditions aerodynamic heating and cooling of aircraft, gas heating in the aerodynamic channel of experimental research facilities, etc. (see USSR Author's Certificate No. 120940, class G01M 9/00, F24J 3/00, publ. 01/01/1959; USSR Author's Certificate No. 354235, class F24J 3/00, G01M 9/00, publ. 01.01. 1972; Patents of the Russian Federation: No. 2150055, class F24J 3/00, publ. 05/27/2000; No. 2144627, class F15D 1/02, F24J 3/00, publ. 20.01.2000; No. 2111094, class. F25B 29/00, publ. 05.27.1999);

- aggregates of the food and metallurgical industries, including for drying and pasteurization of agricultural products, fish processing waste processes (see USSR Author's Certificates: No. 1685543, CL B05B 7/10, publ. 23.10.1991; No. 444919, class F24J 3/00, B01J 1/00, publ. 09/30/1974; Patent of the Russian Federation No. 2063583, class F24H 3/02, F26B 23/00, publ. 10.07.96; No. 2242683, class F24J 3 / 00, published May 20, 2004);

- plants for dispersion, that is, for various types of hydrocarbon and organosilicon liquids processed and divided into fractions, as well as all kinds of solutions, emulsions and suspensions based on them, in a wide range of viscosity and other physicochemical properties (see USSR Author's Certificate No. 5443824 , CL F28F 13/10, B06B 1/18, 01/25/1977; Patent of the Russian Federation No. 2177824, CL B01F 11/02, publ. 10.01.2002);

- in the field of wind, solar, and hydropower, that is, in energy storage and storage devices. The technical result of this group of inventions is to provide the process of accumulating natural energy - solar, wind, wave - without loss of energy over time and increasing the amount of accumulated natural energy (see USSR Author's Certificate No. 1627790, class F24J 3/00, 02.15.1991; USSR Patent No. 1329629, class F24J 3/00, 08/07/1987, US Patent No. 3385287, class 126-247; USSR Copyright Certificate No. 989267, class F24J 3/04, 01/15/1983; USSR Patent No. 13701, class F24J 3/00, 03/31/1930; Patent of the Russian Federation No. 2177081, CL F03D 9/00, F24J 3/00, publ. 12/20/2001).

Since the 90s of the last century, designs of thermal generators have been developed and patented for use as alternative energy sources. Including patents of units based on cavitation and vortex effect, designed for heating systems, without the use of fossil fuels and heating of remote or small-sized communal facilities. As studies have shown, the energy conversion coefficient (hereinafter referred to as KPI) in such units is high, since the loss of electrical energy is completely spent on heating the working medium. According to the conclusion of the Rocket and Space Corporation Energia No. 77-6 / 33 dated 12/01/1994, vortex fluid heaters (VNZh) have an average conditional energy conversion coefficient (KPI) of 23% higher compared to electrode heat generators and 42% higher in comparison with thermal electric heaters.

Numerous technical solutions of heat generators are known, in which cavitation-vortex exposure methods for heating water in hot water supply systems for heat supply of residential, public and industrial buildings, as well as increasing the fluidity of high-viscosity process liquids, are implemented.

In the well-known technical solution according to the patent of the Russian Federation No. 2150055, “Method for heating a liquid and a device for its implementation”, cl. F24J 3/00, author Selivanov N.I., publ. 05/27/2000 (analogue), heat is generated in a heated fluid by mechanical action of a rotating impeller on it with a given linear speed and the application of an oscillating process of a certain calculated frequency.

The apparatus and method described in the invention for heating the liquid is as follows: a working medium to be processed is fed into the cavity of a rotating impeller located coaxially with the stator, through the central hole in the end cap. The processed fluid is discharged into the stator from the impeller cavity through a series of outlet openings uniformly located on its peripheral surface. Liquid is diverted to the circulation circuit or expansion capacity of the heat power system through an opening located on the end wall of the stator diametrically opposite to the cover.

According to one of the preferred variants of the described invention, the discharge of fluid from the cavity of the impeller is carried out in an annular chamber formed by its peripheral surface and the concentric surface of the stator.

Moreover, the radius of the peripheral surface of the impeller and its frequency of rotation are set depending on the selected number of revolutions and the number of outlet openings of the impeller according to empirical relations. Moreover, these ratios are functional relationships between the radius of the peripheral surface of the impeller, the rotor speed and the number of outlet openings formed on the end surface of the wheel.

In another preferred embodiment (according to patent No. 2150055), the execution of the described device and the method of generating heat with the removal of the treated fluid from the annular chamber formed by the peripheral surface of the impeller and the concentric surface of the stator are carried out through a series of outlet openings uniformly located on the concentric surface of the stator, which at the rotation of the impeller are sequentially located against its outlet openings.

In the most effective (according to the description of patent No. 2150055) embodiment of the device for heating the liquid, subject to the optimal ratios between the radius of the peripheral surface of the impeller, the rotor speed and the number of outlet openings formed on the end surface of the wheel, the effect of excessive energy balance is most pronounced. In this case, the achieved effect can be enhanced due to the combined oscillatory effect on the liquid, first when it exits through the openings of the impeller into the annular chamber, and then when it exits the annular chamber through openings on the concentric surface of the stator.

According to the author of the invention, No. 2150055, the rotor of the device may contain several impellers mounted on one shaft, which are connected in series with the fluid flow, with the possible installation of a blade grill in them. Moreover, the system can be looped back to feed part of the treated fluid from the output of the device to its entrance for reprocessing and have an arbitrary spatial orientation of the rotor.

An analysis of the features and kinematic parameters of the described system shows that even when the blades are installed in the internal cavity, there is a mismatch between the main performance characteristics - pressure, productivity and power spent when the flow passes through the impeller, and, accordingly, minimization of efficiency. In addition, the systems described in patent No. 2150055 do not have self-priming and their effect on the working medium until it contacts the impeller is not carried out along the entire fluid path until it meets the inner surface of the rim.

It is known that in blade turbomachines the pressure is an increment of hydraulic energy acquired by each unit of mass or volume of the pumped (transported) medium when it passes the path from the suction to the discharge nozzle of the system. The initiator of the energy increment in the wheel is considered to be a constant pressure increment in the elementary section of the blade (K. Pfleiderer hypothesis), which integrally corresponds to the difference in the specific energies of the fluid between the suction and discharge nozzles.

On the other hand, the total hydrodynamic pressure in a turbomachine blade is the difference between potential and high-speed (dynamic) heads at the entrance and exit of the impeller, respectively. The velocity head is formed as the difference of the squares of the absolute velocities at the outlet and inlet, referred to the doubled value of the acceleration of gravity of bodies in the near-Earth atmosphere.

That is, the speed (dynamic) head fully depends on the difference in the absolute velocities at the outlet and inlet - the higher this difference, the higher the increment of hydraulic energy in the system. However, with the subsequent movement of the working medium to the outlet of the system, into the discharge pipe, the absolute speed has to be drastically reduced, which is carried out in the scapular lattice of the guide apparatus or the inverse diffuser of the housing.

To increase the total potential pressure in the blade machine, it is necessary to strive to increase the difference in the peripheral speeds of the impeller on the outer and inner edges of the blade, that is, to form the blades of the maximum possible length.

Therefore, the proposed technical solution and method according to the patent of the Russian Federation No. 2150055, “Method for heating a liquid and a device for its implementation”, in the described variants (even in the most preferred embodiment) is implemented in the least heat-generating embodiment. The absence of blades minimizes the possible increment of both potential and dynamic pressure. The increment of hydraulic energy in the variants described in the patent is possible only due to centrifugal forces due to the angular frequency of rotation of the wheel. Moreover, the main dominant factor in the movement of the medium in the wheel and the main role in the growth of potential pressure in the device will play a backwater created by an external source of hydraulic energy. It can be a pump — an axial, vortex or large volume pump, operating according to the booster circuit, since the proposed technical solution according to the invention, interpreted as a pump, is not a pump, and also does not have the property of self-priming. Therefore, one of the main disadvantages of the technical solution of the device according to the patent of the Russian Federation No. 2150055 “Method for heating a liquid and a device for its implementation” is the need to use a special pump unit in it to create pressure in the system. Moreover, the increased productivity of the booster pump at the entrance to the system is due to the fact that in the annular cavity of the device, the so-called impeller (according to patent No. 2150055), when the medium is moved, the resulting circulation and countercurrents create resistances that reduce the productivity and pressure in the system. Then, in accordance with the foregoing, the total hydrodynamic head at the system outlet will be the sum of the potential head, depending on the magnitude of the peripheral velocity at the periphery of the wheel and the minimized velocity head due to a drop in absolute velocity due to the circulation of the flow in the wheel. Moreover, a comparison of the centrifugal and working wheels (described in the patent of the Russian Federation No. 2150055, “Method of heating the liquid ...”) of the wheels with equal outer diameters shows the relative advantage of the first one, since the full hydrodynamic pressure of the centrifugal is higher due to the relatively high absolute output velocity ( the peripheral surface of the wheel), the absence of resistance at the outlet and the countercurrents and circulation minimized in magnitude, that is, the relatively high efficiency of the dynamic centrifugal machine and, with tvetstvenno, higher KPI when using it as a heat source.

All this characterizes this device as not sufficiently adequate for its purpose - thermal energy generators, requires adjustment of the structural scheme and selection of the environment for the implementation of the solution.

Installation in the cavity of the impeller (according to patent No. 2150055) of the scapular lattice does not revise the indicated disadvantages in the described patent. The number of holes at the wheel end is much larger than the number of possible blades in centrifugal machines (see Stepanov A.I. Centrifugal and axial pumps. M .: Mashgiz, 1960. - 463 p .; see also: Lomakin A.A. Centrifugal and axial pumps. - M. - L.: Mechanical Engineering, 1966. - 364 p .; see also: Proskura G.F. Hydrodynamics of turbomachines. - Kiev: Mashgiz, 1954. - 417 p. and Proskura G.F. Vortex theory of centrifugal pumps. - Kharkov: Tehizdat, 1931. - 40 p.). An analysis of the relationships and dependencies between the radius of the peripheral surface of the impeller, the rotor speed and the number of outlet openings formed on the end surface of the wheel shows that, subject to the main dimensions for typical centrifugal turbomachines, the number of jumpers forming holes within the same interscapular zone may exceed the number impeller blades two or more times. Therefore, for the impeller, according to the described patent, due to the tightness of the interscapular zone, there is a drop in pressure and, accordingly, productivity. This fact can also be traced from the main equation of L. Euler for the impeller wheel of turbomachines, which connects the head with the absolute and peripheral velocities at the exit of the wheel (provided that the flow enters the wheel without impact). In this case, the serial connection of the impellers for this system is not effective and the possibility of creating cavitation processes in the following, in the order of the wheels from the entrance to the exit from the system, becomes problematic.

In addition, the excitation of oscillations during rotation of the wheel in the device is possible, but the frequency of oscillations will lie in the zone of ultrasonic waves. This is due to the fact that this device is intended for use as an ultrasonic activator and can work (as a construction implemented in industry) in air as opposed to cavitators that generate thermal energy in a liquid medium.

In view of the foregoing, it is clear that this device according to the patent of the Russian Federation No. 2150055, “The method of heating the liquid ...” does not work effectively in the cavitation mode and cannot be designed to be used as a generator of thermal energy with a high temperature gradient between the input and output of the system.

There is also a technical solution according to the patent of the Russian Federation No. 2159901 "Rotary pump-heat generator" authors: Petrakova AD; Sannikova S.T .; Yakovleva O.P., class. F24J 3/00, F25B 30/00, publ. 11.27.2000 (analogue), intended for use as a heat generator by intensifying the process of heating a liquid by increasing the frequency of hydraulic shocks and ensuring stable hydrodynamic cavitation. In this case, cavitation occurs by slowing down the jets when they are throttled through nozzles formed in the form of Venturi nozzles.

The task of intensifying the heating of the working medium, according to the description of the patent, is achieved by the fact that in the rotary two-flow pump-heat generator containing a diffuser body with a pipe for supply and a pipe for draining liquid, there is a double-flow impeller, the output cylindrical part of which is surrounded by a circular ring rotor, bearing a number of circular cylindrical nozzles in the form of Venturi nozzles. At the calculated distance from the wheel exit section, an annular closed stator is coaxially located, in which nozzles in the form of Venturi nozzles, which are turned in the radial direction, are also formed, with a sharp stepwise expansion of the output (peripheral) part of the cylinder.

The cylindrical shape of the holes of the nozzles of the rotor ensures the occurrence of cavitation processes in the wall zone of the nozzles at the inlet of the flow into the nozzles and a sharp decrease in pressure below the pressure of water vapor, which leads to intensive release of bubbles. As the transit jet moves along the length of the Venturi nozzle from the inlet to the periphery, the pressure increases along the flow cross section and the collapse of the bubbles leads to the first wave of pressure overflow and temperature evolution in the medium being treated. With further rotation of the rotor and overlapping of the nozzles of the inner zone by the walls of the stator in the transit stream, the pressure sharply increases due to direct hydraulic shock, which also leads to the collapse of cavitation bubbles and additional heat. When the nozzle axes coincide, the transit flow passing through the venturi nozzles in the stator, due to the sharp expansion of the cross section and local pressure loss, causes an increase in cavitation and heat generation. According to the description of the patent of the Russian Federation No. 2159901 "Rotary pump-heat generator" by varying the flow rate of the processed medium, as well as by the pressure at the inlet and outlet of the device, a self-oscillating mode of operation of the system can be created, which (according to the authors) implies a decrease in energy consumption in the system with increasing heating rate processed medium.

The proposed technical solution and its implementation requires energy to maintain a self-oscillating regime in the system, that is, the presence of additional units for pumping the medium to be processed and optimizing the necessary performance at the system entrance. Similarly, the requirement to vary the pressure at the outlet of the system also requires special devices for controlling the specified parameter, the presence of which (see patent No. 2159901 "Rotary pump-heat generator") is specified in the description of the invention. In general, to maintain and adjust the heat generator system itself, both energy consumption and the presence of direct and feedback of the system with the control computer are required. In the aggregate, the task set by the inventors of patent No. 2159901 "Rotary pump-heat generator ... creating a simpler device ..." is not implemented in the framework of the described technical solution.

In addition, the entire system loses its operability with the relative displacement of the axes of the Venturi nozzles relative to each other due to its exit from the self-oscillating regime. It requires automatic readjustment and adjustment of the system to a mode that is optimal and most economical for the proposed solution.

Also known is a technical solution according to the patent of the Russian Federation 2061195, “Method of heat dissipation in a liquid”, cl. 6 F24J 3/00, similar in purpose to the claimed patent, in which effective heat dissipation in a liquid is provided by intensification of the cavitation process by creating a gas cushion and a self-oscillating process with a change in its volume and pressure of the liquid. The disadvantage of this method is the difficulty of regulating a process that requires the use of computers. The use of a centrifugal nozzle as a cavitator reduces the durability of the device due to its destruction by cavitation erosion. In addition, the disadvantages of the known apparatus also include the instability of the characteristics of the cavitation process, the difficulty of controlling and maintaining operating parameters to ensure its functioning modes within the framework of the requirements of the technological task.

Closest to its technical solution to the claimed invention, the patent of the Russian Federation No. 2054604 "Method for producing energy", author Kladov AF (CL F24J 3/00, G21B 1/00, application No. 93033524/25, application filing date - 07/02/1993, publ. 02/20/1996, prototype), in which the process of increasing heat in the proposed cavitation unit is associated with the effect on the pumped substance with variable and constant pressure.

The device according to patent No. 2054604 “Method for producing energy” contains two or more working chambers connected in series, in each of which impellers of a centrifugal pump with rotors fixed on the periphery in the form of perforated rings are installed. Coaxial to the rotors in the housings of the working chambers opposite each rotor is a stator made in the form of a perforated ring. In aggregate, according to the invention, the serial connection of the working chambers and wheels, with perforated rotor rings and ring stators with radial holes fixed on their periphery, represents an ultrasonic activator. The working chambers are interconnected by means of diffusers. The last working chamber is connected to the first chamber by a circulation circuit. According to the description of the patent, the processed substance, for example water, is supplied to the ultrasonic activator, and during rotation the impeller of the centrifugal pump gives it kinetic energy, which is partially converted into static pressure in the channels of the guiding apparatus (diffuser, which is not shown in the patent), and partially in alternating pressure - when passing the holes of the perforated annular rotor of the holes of the perforated stator.

Depending on the selected liquid, its temperature and the calculated values of static and variable pressures that satisfy the above dependencies, the design and technological parameters of the ultrasonic activator are established and maintained.

According to the above description, in patent No. 2054604, cavitation bubbles form during the action of a half-period of a half-period of a negative half-wave of alternating pressure on the liquid in the liquid in the treatment zone. During the action on the liquid of the next half-cycle of the positive half-wave of alternating pressure, the cavitation bubbles are compressed. By the end of this half-cycle, the bubbles store kinematic energy, which is determined by the pressure difference acting on the bubbles from the outside and from the inside. Outside, the sum of the alternating and static pressures acts on the bubbles. Inside the bubbles, the pressure of the saturated vapor of the liquid acts. In addition, other forces determined by the physicochemical properties of the liquid, as well as the absolute values of the claimed output parameters, also influence the movement of the bubbles.

At the moment of collapse of the bubbles, the kinetic energy is converted into the energy of collision of elementary particles (according to the description of patent No. 2054604). The energy released during the collapse of the bubble is several orders of magnitude higher than the binding energy of elementary particles (nucleons) in the nucleus. As a result of a collision of nuclei in the conditions of the proposed method, an interaction occurs between the elementary particles that make up the nucleus. The energy released in the reactions controlled by the described method between elementary particles is converted into thermal energy in a liquid, and it is removed from the treatment zone with a flow of the working substance.

The main disadvantages of the device according to patent No. 2054604 “Method for energy production” is the occurrence of large axial forces directed towards the suction fitting, variable in magnitude, as well as the absence of a discharge unit in the flow part to compensate for them. As a result, this device, in the above arrangement, can only be used as an ultrasonic activator when operating in air due to the significant difference between the hydrodynamic and aerodynamic forces. In addition, as is known from long-term studies of sectional turbomachines that do not have a longitudinal connector, their assembly should be carried out by elementwise balancing of the parts of the flow part, determinism of the distribution of the impeller wheels on the shaft, and ensuring the mutual alignment of the mating parts (see Aliev N.A. The development of the scientific foundations of creating housing-sectional shaft pumps of increased durability / Dissertation of the doctor of technical sciences: 05.06.06. - D., 2006. - 375 p .; see also: Aliev N.A. oversized rotor masses as a basis for reducing vibration load of case-sectional pumps during assembly // Problems of operation of mine stationary installations: Nauchnykh Praznik Zbirnik - Donetsk: NIIIGM named after M.M. Fedorov, 2004. - Vip. 99. - S.101- 117). Accordingly, the operation of the above device can be ensured exclusively with high manufacturing technology and assembly only at the initial stage (in the presence of an unloading unit) and chemical-thermal methods of hardening the parts of the flow part.

In addition, the arrangement of the impellers, with the rotors fixed on the periphery, with a coaxial installation of an annular stator with perforation opposite each of them, violates the condition of continuous and sequential transportation of the working medium between the stages of the unit due to the violation of the functional relations of the continuity equation. This, in turn, makes the structure inoperative with a constant outer diameter of the impellers, up to a complete loss of pressure and, accordingly, the stability of the conditions for the occurrence of cavitation processes with heat generation. Changing the outer diameters of the impellers in the direction of increasing requires the coordination of the geometry of each vanes of the wheel, the vanes of the guide vane and the return vanes of the stage casing by themselves. In turn, this requires the presence of a pre-assembly cycle in the assembly process for positioning and ordering each stage with the wheel strictly to a specific place on the unit shaft, and additional energy consumption.

In the aggregate, the proposed solution for patent No. 2054604 “Method for energy production” is not technologically advanced both in the production of its elements and in pre-assembly preparation and assembly, cumbersome during commissioning and operation. All this as a whole does not imply the possibility of using it as a source of heat generation without the use of fossil fuels, as well as widespread introduction into the heat and power industry.

Analysis of analogues and the main prototype allows us to conclude that in these inventions the problem of heat generation through the use of cavitation and oscillatory processes in the medium being processed is not quite efficiently solved.

In addition, their use as alternative heat generators in circulating heating systems is not advisable, since they are energy-intensive, bulky and difficult to operate.

Information disclosing the essence of the invention.

The basis of the invention is the task of improving the operation of thermal cavitation generators by stabilizing and increasing the intensity and energy saturation of cavitation flows of the processed rheological media, including water. The technical result of the proposed design solution of the heat generator is the high stability of the operating characteristics of cavitation processes, an increase in the intensity of the heat release process due to an increase in the number of cavities of generation of cavitation and hydraulic shocks on the oncoming flows of the processed medium while minimizing the energy costs of the drive system and simplifying the control of the unit.

The problem is solved in that in the thermal cavitation generator, consisting of a rotor formed by the sequential installation of centrifugal and cavitation wheels half-open type, guide vanes with a spatula grill, housings with a return vanes diffuser, suction and discharge covers, brackets with support units, cavitation wheels are made in the form of a disk perforated with conoid-cylindrical nozzles, with radial-radial blades framed at the end by a cylindrical perforated rim m, the guiding apparatus of the cavitation stage is made with perforation in the interscapular zone, and the support on the cavitation stage is created by a conical nozzle nozzle installed at the outlet of the medium to be processed from the return vaned diffuser of the precavitation stage body. In this case, the total increase in the temperature of the medium to be treated in a given time interval and the pressure in the circulation circuit of the system is formed by a group combination of centrifugal and cavitation wheels on the rotor in the energy conversion unit.

This technical solution of the thermal cavitation generator, formed by installing a centrifugal wheel to suction the medium from the receiver (the supply pipe of the circulation circuit or the cavitation tank), converts the energy of rotation of the shaft into a hydrodynamic pressure, part of the kinetic pressure into a potential stage in the guiding apparatus and the body diffuser, swirl flow through a conical nozzle nozzle integrated into the scapular diffuser of the casing and feeding it to the scapular (axle th) lattice cavitation wheel with perforated radically disk, allows to obtain an increase in number of foci generating cavitation and pressure shocks in colliding jet flows throttled through conoid-cylindrical perforation nozzles, which leads to an abrupt increase of the temperature gradient in the stage.

In addition, this technical solution of the thermal cavitation generator, depending on the required level of the thermal gradient and the relative rate of temperature increase in a given time interval, allows it to be formed by a sequential combination of centrifugal and cavitation wheels in a stage, their grouping in the energy conversion unit, and also by varying the number of such blocks , with the implementation of efficient and targeted conversion of mechanical energy into heat in accordance with the requirement and functionality nym appointment consumer.

Depending on the specified requirements, one, two (or several) blocks of centrifugal and cavitation wheels can be installed on the rotor shaft of a heat cavitation generator, sequentially or with a grouping of them by working functions, including a cavitation block between centrifugal wheels - suction and discharge, or a centrifugal unit consisting of two or more impellers at the suction, with cavitation wheels consisting of several such impellers at the discharge.

If necessary, to increase the temperature of the circulation circuit, a set of two or more cavitation wheels located in a block on the unit shaft in series allows you to create a cumulative increase in the temperature of the medium being processed, proportional to the temperature gradient of each of the wheels.

The need to increase the pressure in the system by which the object is supplied with heat in the proposed heat generator can be realized by installing two or more centrifugal wheels in series after the block of cavitation wheels, which allows overcoming the resistance of the circulation system with the necessary pressure increase.

The variation of the temperature or the gradient of temperature fields in sections in a heat generator can be carried out by changing the diameter of the cylindrical channel of the conoid-cylindrical nozzles, forming the perforation of the cavitation wheel, as well as by varying the number of wheels or the thickness of the wheel disk and, accordingly, the path length of the throttled medium. By varying the diameter of the cylindrical channel of the nozzle of perforation of the guiding apparatus of the cavitation stage, as well as by the solution of its conoidal parts, it is also possible to change the intensity of the heat release process in the cavitator assembly. With a corresponding difference between the inlet and outlet nozzles forming the nozzles, it is possible to activate the cavitation process, which directly depends on the flow rate of the liquid medium through the heat generator, as well as on the presence of zones with reduced pressure in it, that is, on the geometry of the perforation holes, if any in them suddenly expanding sections.

The above characteristics characterizing the invention are essential, since in the aggregate they are sufficient to ensure operability and achieve the technical problem being solved, and each separately is necessary to identify and distinguish the claimed thermal cavitation generator from similar solutions known in the art.

Thus, a new set of common (known) and distinctive (new) from the prototype of the essential features that characterize the thermal cavitation generator is sufficient in all cases to which the scope of legal protection applies, since it solves the problem.

The indicated features characterizing the invention are not mandatory, but, according to the applicant, are the best and do not exclude the possibility of another specific equivalent implementation of the heat generator within the specified essence of the invention.

The causal relationship of the distinctive (new) features in their interaction with the known (common) features in providing new properties of the subject of the invention, due to the technical task, is as follows.

Due to the fact that in the heat cavitation generator the flow part is formed by sequential installation of centrifugal and cavitation perforated wheels on the rotor of the unit, with radial beam (axial) blades framed at the end with a cylindrical perforated rim, and the guiding apparatus of the cavitation stage is made with perforation in the interscapular zone, with the creation of a backwater to the cavitation stage with a conical nozzle nozzle from the scapular diffuser of the precavitation stage body, conditions are created is the number of foci of generating cavitation and pressure shocks secured abrupt increase of the temperature gradient in the stage, creating conditions of intensive growth of the treated fluid temperature with simultaneous circulation in its circuit.

In addition, this technical solution of the thermal cavitation generator allows you to vary the temperature, pressure and velocity of the medium being processed, both by changing the geometry of the nozzles of the wheels and guide vanes, and by a sequential combination of centrifugal and cavitation wheels, as well as their location on the rotor. This level of mobile change in the operating parameters of the heat generator by changing the wheels, their number and installation location on the rotor of the unit characterizes the proposed solution that is easily adaptable to the required operating conditions of the circulation circuit, and also characterizes a system that is convenient to operate and operate.

To reduce the erosive effect of cavitation on the flow part of the unit, cavitation processes are organized in the central part of the unit with the creation of a vortex fluid flow at the periphery from the body elements of the unit.

Using the proposed cavitation heat generator allows you to provide hot water and thermal energy to objects remote from the main pipelines, while the environment is not polluted by the combustion products of fossil fuels in places of heat energy production.

The invention is further explained in the detailed description of an example of a specific implementation of its best option with reference to the accompanying drawings.

The list of drawings of the invention

Figure 1 shows a thermal cavitation generator, a General view, a cross section; the rotor of the generator is formed by the sequential installation on the shaft of centrifugal wheels for suction and discharge, when placing a cavitation perforated wheel between them. The wheels with guide vanes and their spatula grill were mounted in a cylindrical casing with a return vaned diffuser, and the structure was closed by means of suction and discharge covers, tightened by anchor rods, and placed outside the heat-affected zone of the brackets with support nodes.

Figure 2 shows a thermal cavitation generator, a view of the cavitation block, a cross section; elements of the cavitation stage are made in the form of a perforated disk with conoidally cylindrical nozzles and radial beam (axial) blades framed at the end by a cylindrical perforated rim; in this case, the guiding apparatus of the cavitation stage is made with perforation in the interscapular zone, and the support on the cavitation wheel is created by a conical nozzle nozzle installed at the outlet of the medium to be processed from the return vaned diffuser of the precavitation, centrifugal stage housing.

Figure 3 shows a thermal cavitation generator, a view of a cavitation block with an increased temperature field; view of the flowing part of the unit, while the cavitation unit is composed of two or more cavitation wheels with perforated guide devices located between the centrifugal steps with the wheels on the suction and discharge into the circulation circuit.

Figure 4 shows a thermal cavitation generator, a view of the cavitation block and centrifugal stage with increased pressure on the discharge in the circulation circuit; while the cavitation block is composed of two (or more) cavitation wheels with perforated guide vanes located between the centrifugal steps with two (or a large number) of wheels on the suction and discharge into the circulation circuit.

The list of symbols and names of elements of the invention

1. Val

2. Suction cover

3. Discharge cover

4. Generator stage housing

5. Spatula diffuser, stage housings

6. The cylindrical section of the interface of the housing

7. Interstage seal

8. The directing device of a centrifugal step

9. Spatial lattice of the directing device of centrifugal step

10. Wheel centrifugal, radial, suction

11. Wheel centrifugal, radial, edged, forcing

12. Cavitation wheel, perforated

13. The blade of the wheel cavitation

14. The nozzle is conoidal-cylindrical, the perforation of the cavitation wheel

15. The bell is conoidal, inlet, cavitation wheel perforation nozzle

16. A bell conoidal, output, a nozzle of perforation of a wheel of cavitation

17. Channel cylindrical nozzle perforation wheel cavitation

18. Conical nozzle nozzle

19. Front bracket

20. Rear bracket

21. The guiding apparatus of the cavitation stage with perforation

22. Perforated cylindrical rim.

Information that confirms the possibility of carrying out the invention

The technical solution of the heat cavitation generator described above allows the formation of a stable and constant heat generation in the unit due to the development of numerous cavitation centers and hydraulic shocks in the medium being throttled through conoid-cylindrical nozzles, which leads to an abrupt increase in the temperature gradient in the stage and an increase in intensity , as well as the energy saturation of cavitation flows with minimizing the energy consumption for the drive system and maintaining p bochih process characteristics.

The thermal cavitation generator (Fig. 1) contains a shaft 1, suction and discharge covers 3, cylindrical bodies 4, forming generator steps and supporting diffuser vanes 5 on the inner end surface of the wall, with each section centered and planted together by means of cylindrical bores 6, with sealing the inner cavity of the heat generator with seals 7.

The inner cylindrical surface of the housing 4 is a support of the outer cylinder of the guide apparatus 8 with a blade grill 9, by which the flow of the processed medium is transmitted to the diffuser of the housing 5 and then to the next stage of the heat generator.

The rotor of the thermal cavitation generator is formed by sequentially installing centrifugal, radial impellers 10 at the suction, and at the discharge, the edging wheel 11 (Fig. 1), the flow part and the blade of which corresponds to the design parameters and operating conditions of the circulation circuit of the heated system, as well as perforated cavitation (cavitation) wheels 12.

Cavitation perforated wheel 12 is a disk with radial beam blades 13 — an axial wheel of a semi-open type (Fig. 2), the main part of which in the interscapular region is formed by conoid-cylindrical nozzles 14 with the maximum possible number of them in the interscapular region. The conoidal-cylindrical nozzle itself is formed by the inlet 15 and outlet 16 — conoidal sockets connected to each other by a cylindrical channel 17. The operability of the thermal cavitation generator, as well as its KPI, directly depends on the total number of nozzles 14 on the cavitation wheel 12, as well as the stiffness of the system and stability of geometric clearances during operation of the unit. The organizing factor that ensures the efficient operation of the heat generator in terms of stiffness and stabilization of the gaps during operation of the unit is to minimize the deviation of the real axis of the shaft 1 of the unit from its geometric prototype and the longitudinally-transverse vibration displacement of the elements of the flow part. Considering that the design and construction of the heat generator in the form of series-conjugated housings 4 predetermines the sectional flexibility of the assembly system, an important factor in the operation of the heat generator is the organization of uniformity and concentricity of radial clearances along the end seals, end clearances between the wheel blades and the end face of the conical nozzle nozzle 18 (Fig. .2), which creates a backwater on the cavitation wheel 12. Such requirements for uniformity and constancy of gaps for a heat generator, etc. predetermines removal of the support units outside the working area of the unit, special technological activities in the organization of tooling brackets front 19 and rear 20, and the model features the bearing assemblies to eliminate the influence on them of the temperature of the machine mode. In addition, remote support units located in the cylindrical consoles of the brackets 19 and 20, positioning the shaft 1 when assembling the unit in horizontal and vertical planes, must ensure strict alignment of the axes of the bearings, which is also a guarantee of equal gaps and a constant distance between the opposing streams of jets passing through the nozzle. At the same time, for such dynamic turbomachines - heat cavitation generators, equal gaps for the entire service life, minimization of technological imperfections and vibration loads are guaranteed when the wheels and elements of the flow part of the unit are dynamically balanced at operational speeds with a deterministic assembly (see Aliev N.A. Investigation of forced oscillations of rotors sectional machines of dynamic action // Progressive technologies and engineering systems: International collection of scientific papers c. - Donetsk, 2004. - Issue 27. - C.3-11; see also: Aliev N.A. Vibrodiagnostics of casing-sectional pumps with the predicted distribution of unbalanced rotor masses / Science of the Donetsk National Technical University. - Donetsk, 2004. - Vip. 83. - P.225-235; see also: Aliev N.A. Determinism of the distribution of unbalanced rotor masses as a basis for reducing the vibration load of casing-sectional pumps during assembly // Problems of operation of mine stationary installations: Zernik naukovyh prats . - Donetsk: NIIIGM them. M.M. Fedorova, 2004 .-- Vip. 99. - S.101-117).

The number of blades 13 on the cavitation wheel 12 directly depends on the technical requirements for system performance and is associated with the fulfillment of the continuity of the flow when it passes through the diffuser of the casing 4 precavitation stage. Considering that on a radial-beam (axial) scapular system, the pressure is two, and in some cases three times higher than the pressure relative to the centrifugal stage with cylindrical vanes, if the outer diameters of the wheels are equal, then the part of the flow that has not passed through the conoid-cylindrical system nozzles 14 on a cavitation perforated wheel 12, is transported through a guide perforated apparatus 21 to meet the jets passing through the system of perforation of the cavitation wheel 12. This embodiment of the cavitation stage drives rise in colliding streams of hydraulic shocks and self-oscillatory mode site work, which also causes additional turbulence between cavitation wheel 12 and guide vanes 21 with an increase in heat generation.

Figure 2 shows a thermal cavitation generator, a view of a cavitation perforated wheel 12, consisting of a perforated disk with radial beam (axial) blades 13, framed around the periphery of a cylindrical perforated rim 22. The guiding apparatus 21 of the cavitation stage is made with perforation in the interscapular zone, and the support on the cavitation wheel is created by a nozzle conical nozzle 18 mounted at the outlet of the medium flow from the scapular diffuser of the casing 4 of the precavitation centrifugal stage . The perforation of the cavitation wheel 12 is formed by conoid-cylindrical nozzles 14 formed by the inlet 15 and outlet 16 — conoidal bells, the diameters of which are selected from the condition of continuity of the flow over the nozzle section, but with the expansion of the outlet section relative to the inlet and interconnected by a cylindrical channel 17.

Figure 3 shows a thermal cavitation generator, a section along the flow part of the unit, with the possible implementation of the unit with a high temperature field at the outlet of the system.

For this purpose, the cavitation block is composed of two cavitation perforated wheels 12, with perforated guide vanes 21 located between the centrifugal steps with wheels - on suction 2 and forcing 3 into the circulation circuit.

Figure 4 shows a cross-section along the flowing part of a thermal cavitation generator, composed of two cavitation perforated wheels 13 forming a heat block, and a centrifugal stage with increased pressure on the discharge into the circulation circuit. To implement the requirement of increasing the pressure in the system, two centrifugal impellers 3 are installed on the discharge, which leads to an increase in pressure at the entrance to the circulation circuit.

This technical solution of the thermal cavitation generator allows you to form the flow part of the unit, depending on the requirements of the operating mode of the installation for thermal loading and pressure by varying the number of cavitation and centrifugal stages on the suction and discharge. In this case, the temperature gradient and the change in the intensity of the heat release process in the cavitation stage (ceteris paribus) varies by changing the diameters of the cylindrical part of the nozzles, the thickness of the disk of the cavitation wheel, the difference in the sockets of the conoidal inlet and outlet sections, and also by changing the diameter of the cylindrical channel of the nozzles of the perforation of the guiding apparatus of the cavitation steps. In this case, the difference or narrowing between the inlet and outlet sockets forming the nozzles activates the cavitation process and leads to an increase in the temperature gradient in the cavitation stage.

The universality of the claimed technical solution of the heat generator, its adaptation to an external source-consumer, control efficiency, as well as optimization of operation and reliability of the unit as a dynamic system, is directly related to the ability to form its rotor in series, from centrifugal and cavitation perforated wheels in a stage, rearranging them in the energy conversion unit with variation of the total number of units of the unit depending on the technical requirements of the working consumer.

Thermal cavitation generator, designed as an autonomous system, converting mechanical energy into heat in locally closed heat supply systems, without the use of fossil fuels or using in technological processes requiring heating of the processed media, works as follows.

Thermal cavitation generator through a suction fitting, a receiving pipe and a valve is integrated into the circulation circuit or receiver to collect the medium to be processed and supply it to the flow part of the unit. The flow part of the heat generator is formed of a centrifugal stage with a radial wheel, a guiding apparatus in which the high-speed pressure is converted to static pressure and a return vaned diffuser of the stage casing, at the outlet of which a nozzle conical nozzle is installed. When the flow of the medium is processed through the nozzle conical nozzle, due to a change in the cross-sectional area, the velocity head at the nozzle exit sharply increases, and the stream, entering the cavitation wheel disk, is throttled through the conoid-cylindrical nozzles located in the interscapular zone and organizing the cavitation wheel perforation . Radial (axial) blades are formed on the disk of the cavitation wheel, which act as elements that communicate additional kinetic energy to the flow that has not passed through the conoid-cylindrical nozzle and directs it to the cavitation stage apparatus. The ends of the radial (axial) blades are framed around the periphery with a cylindrical perforated rim that creates resistance to flow that has not passed through the wheel disk.

The velocity of the outflow of jets from conoidally cylindrical nozzles and the occurrence of cavitation processes are associated with the difference between the cylindrical channel and the outlet conoidal nozzle socket. Moreover, the generation of thermal point heat sources is directly proportional to the number of such nozzles and the difference in diameters between the cylindrical channel and the conoidal nozzle socket. When the cavitation wheel rotates, the excess flow passing through the perforated grating of the rim vanes framing and falling into the guiding apparatus of the cavitation stage creates circulating vortex flows on the oncoming jets throttling from the nozzles of the wheel, which also cause the formation of cavitation bubbles and generate heat in the stage.

The movement of the nozzle throttling flow from the cavitation wheel and the coincidence of the perforation jumpers on the guiding device of the cavitation stage form water hammer in the space between the rotating wheel and the device, as well as fluctuations proportional to the number of nozzles on the wheel and its rotation speed.

The combined effect of system oscillations, water hammering and cavitation processes that occur in conoidally cylindrical nozzles leads to the generation and generation of foci of heat generation with the possibility of obtaining a constant temperature gradient in the stage. The level of abnormal heat generation in the generator can vary by changing the diameter of the cylindrical channel of the conoidal-cylindrical nozzles, the diameter of the conoidal sockets, the variation in the number of wheels, the thickness of the disk and the path length of the throttling of the medium to be treated, as well as the cone angle of the nozzle nozzle.

The invention is not limited to the embodiments described and shown in the drawings, but can be changed, modified and supplemented within the scope defined by the claims.

The invention was tested during bench and operational tests and the test results fully confirmed its technical and economic efficiency, as well as the feasibility of widespread use. The inventive heat cavitation generator can be put into serial production in the factory and will be widely used in heat supply systems without the use of fossil fuels, heating of stationary stationary objects, as well as technological processes that require heating of the working environment during hydraulic fracturing.

Claims (2)

1. Thermal cavitation generator, consisting of a rotor formed by the sequential installation of centrifugal and cavitation wheels half-open type, guiding devices with a spatula grill, housings with a return vanes diffuser, suction and discharge covers, brackets with support units, characterized in that the cavitation wheels are made in in the form of a disk perforated with conoid-cylindrical nozzles, with radial-radial blades framed from the end by a cylindrical perforated rim, directing The cavitation stage apparatus is perforated in the interscapular zone, and the support on the cavitation stage is created by a conical nozzle nozzle installed at the outlet of the medium to be processed from the return vaned diffuser of the precavitation stage body. 2. The thermal cavitation generator according to claim 1, characterized in that the total temperature increase of the medium to be treated in a given time interval and the pressure in the circulation circuit of the system is formed by a group combination of centrifugal and cavitation wheels on the rotor in the energy conversion unit.

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