CN106661875B - Transonic two-phase reaction turbine - Google Patents

Abstract

A transonic two-phase reaction turbine for use with low and high temperature fluid flow media, the turbine comprising at least two wheels configured to rotate in opposite directions, at least one of the at least two wheels being equipped with one or more kinetic energy harvesters.

Description

Transonic two-phase reaction turbine

Cross Reference to Related Applications

This application claims the benefit of U.S. patent application No.62/019091, filed on 30/6/2014, which is incorporated herein by reference in its entirety.

Technical Field

The present invention relates to the field of kinetic and thermal energy collection, mixing, vacuum and pumping technology, where an efficient process of kinetic and thermal energy collection can be organized and thrust and vacuum generated by exploiting the kinetic energy between liquid particles in a closed or open circuit.

Background

Known methods of heating liquids include an electric or steam driven pump, a heat exchanger and a spray device that are indirectly and directly in contact with heat Energy supplied from a boiler or district heating system, where the liquid is heated by a steam or hot water supply (see, for example, reference 1: ai. orlistat of "demonstration of Performance and Energy Efficiency of a Fisonic device at a joint Edison testing Facility", austria, n.y. Energy research and development, Report No. 20346 (NYSERDA Report #20346) heated water is delivered to a consumer (end user), after delivering heating Energy to the user, cooled liquid/condensate collected in a condenser is delivered back to the heat source by a pump in a closed loop and the cycle repeats again, a makeup fluid is provided to the system. This method consumes a considerable amount of thermal energy and pumping energy for heating and transporting the liquid.

Many injection-type devices for heating and transporting liquids, vapors, gases and solid materials are used in the industry. These injection type devices include Venturi de-superheaters (Venturi de-superheaters), steam injectors, injection exhausts and compressors, injectors and injection vacuum pumps.

A typical injection-type apparatus consists of three main parts: a converging (working) nozzle surrounded by a suction chamber, a mixing nozzle and a diffuser. The working (moving) and injected (entrained) streams (stream) enter the mixing nozzle where the velocity is equalized by the energy exchange and the pressure of the mixture is increased. The combined flow enters the diffuser from the mixing nozzle or nozzles, where the pressure is further increased. The diffuser is shaped to gradually reduce the velocity and convert the energy into discharge pressure with as little loss as possible. Injection-type devices transfer the kinetic energy of the working stream to the injection stream by direct contact without consuming mechanical energy. Injection type devices operate at high expansion and medium or high compression ratios and require continuous power.

During the interaction of two streams with multiple velocities, an increase in entropy of the mixed stream occurs (as compared to reversible mixing), resulting in a decrease in pressure of the discharge stream. Thus, typically, the discharge pressure of an injection-type device is higher than the pressure of the injection stream, but lower than the pressure of the working stream.

A disadvantage of the ejector-type device is that it uses a high level of power to perform work, which reduces the outlet pressure, significantly reduces the effectiveness of the initial energy input ratio and requires continuous motive power. Therefore, these devices cannot be used to boost the pressure to higher output levels. Other devices such as those operating based on the so-called fisherinc technology may utilize lower energy inputs and boost the initial thrust and heat loads. This is achieved by the fisherinc technology design by exploiting the very low mach number of the two-phase flow and taking the trace (< 0.1%) system's thermal energy and converting it into kinetic thrust.

In the fisheric device ("FD device"), the injected water/fluid enters the mixing chamber at a high velocity parallel to the velocity of the working stream. The injected water/fluid is usually supplied through a narrow circumferential channel around the working nozzle. The mixing chamber typically has a conical shape. The optimized internal geometry of the FD device causes the working and injection streams to mix and accelerate, creating transonic conditions, breaking up the stream into tiny particles and changing the state of the mixed stream to plasma conditions, and finally converting a tiny fraction of the thermal energy of the stream into physical thrust (pump head), with the discharge pressure higher than the pressure of the mixed stream. The main reason behind this phenomenon is that a homogeneous two-phase flow has a high compressibility. The homogeneous two-phase flow proved to have a greater compressibility than the pure gas flow. Thus, in a homogeneous two-phase mixture, thermal energy can be more efficiently converted to mechanical work, particularly in transonic or supersonic modes.

The speed of sound in such systems is much lower than in liquids and gases. As can be seen from fig. 1, the minimum sonic velocity occurs at a flow volume ratio of 0.5. An important feature of FD devices is also the independence of the discharge stream from changing parameters (e.g., backpressure) downstream of the end user system, indicating that the FD device is producing supersonic flow and there is no downstream communication (or so upstream) through the mach barrier.

Referring to FIG. 1, it can be seen that the ratio β equals zero when there is no liquid-ratio equals 1 if there is no gas-when there is 50% liquid and 50% gas (two-phase flow) -ratio β equals 0.5, the sonic velocity is much lower than in gas and in liquid.

Wherein: k is an isentropic index, equal to the ratio of specific heat (specific heat); p is pressure; p is the density of the medium. To determine the isentropic index, the following equation was developed:

wherein: k is a radical of_gIsentropic index of the gas in the mixture; ε is the critical ratio of pressure.

As a result of the exchange of motion pulses between the working stream and the injection stream, the speed of sound in the mixing chamber decreases. The flow at the entrance of the mixing chamber (throat) has a velocity equal to or greater than the local speed of sound. As a result of the flow deceleration, the temperature and pressure at the outlet of the mixing chamber increase. At the saturation temperature of the mixture, the pressure becomes higher than the saturation pressure. The discharge pressure may be increased several times over the pressure of the working medium at a particular design geometry. The liquid phase in the mixing chamber has a foam-type (plasma) structure with a very highly turbulent surface area, and therefore the FD device is very small in size compared to conventional surface-type heat exchangers. Note that FD is a constant current device.

The significant difference in the above process occurs at small implant coefficients. Reducing the flow rate of the injected water/fluid at a constant steam flow rate causes the water temperature to increase to the saturation temperature corresponding to the pressure in the mixing chamber and its pumping performance decreases proportionally due to the shortage of water for condensing all the steam, while the heat exchange operation of the FD device continues. This mode determines the minimum injection coefficient. In this mode, the operational and geometric factors affect the characteristics of the FD device. As the injection coefficient increases, the water temperature in the mixing chamber decreases as the flow rate of injected water (as a result of the reduced back pressure) increases. At the same time, the water pressure decreases due to the increased velocity in the mixing chamber. Increasing the flow rate of the injected water causes the pressure at the inlet into the mixing chamber to decrease to a saturation pressure corresponding to the temperature of the heated water. The reduction in back pressure does not result in an increase in water flow rate, since no further pressure drop in the mixing chamber is possible. The pressure drop determining the flow rate of the injected water cannot be increased. Further reduction of back pressure under such conditions causes the water in the mixing chamber to flash.

Cavitation (cavitation) of the water in the mixing chamber determines the maximum (limiting) injection coefficient. It should be noted that the operating condition is the operation mode of the FD. FD operates at high expansion and small compression ratio.

Recent analysis and testing of FD led to the conclusion that the internal (inter-particle) energy to work conversion of superheated liquids can be achieved in the presence and absence of "cold" thermal conductors. Furthermore, at a certain pressure value and certain internal geometrical parameters of the inlet device, the "cold" liquid itself becomes a two-phase medium before the pressure surge. From this phenomenon, one of the main important conclusions follows, namely that the internal (interparticle kinetic) energy of the liquid can be converted into useful work under the desired conditions.

In addition to the above, other subject matter disclosed herein relates to the production of mechanical work, particularly direct contact heat exchangers for the production of heat, and hydraulic, pneumatic and steam turbines for driving generators, hydraulic pumps, compressors, thermal and two-phase pumps.

Many buildings in the united states and the world use steam for space heating, cooling and domestic hot water supply. Steam condensate is sometimes returned to the steam generation source or discharged to a municipal sewer system. To reduce the condensate temperature from 220F to about 110F (city sewer requirements), the condensate is mixed with cold drinking water. Such systems operate with considerable electrical, heat and water losses and sewage discharge rates. All discharge rates are evaluated and compensated.

Existing alternative sources of wastewater for electricity production include large scale steam (fossil and nuclear), reciprocating internal combustion and diesel power plants, chemical processes, and geothermal, solar thermal and bottoming cycles for various industries. Typically, the energy in the boiling waste water is transferred to a thermodynamic working fluid (binary cycle) to produce electricity. Because the water or other waste stream is only at moderately high temperatures and pressures, the working fluid operates with low energy conversion efficiency (15 to 20%) in the two-phase region and often suffers from poor durability.

In 2000, the california energy commission sponsored a project (CEC-500-. The water used by the turbine was heated to 435 ° F and 350 psig. The main difference between the proposed invention and the above turbine is the use of renewable waste liquids and gases, readily available at low temperature, and the application of advanced transonic nozzles capable of generating very high discharge pressure thrust.

Two-phase counter-flow turbines for obtaining mechanical energy are known, including radially outward flow turbines having a rotor with nozzles extending from an internal inlet passage to the rotor periphery, wherein the nozzles have a substantially constant pressure drop per unit length, a first order surface continuity along each nozzle surface, and a nozzle profile that allows two-phase flow without substantial lateral acceleration. The turbine also has an outer casing that is rotated by the flow entering the housing opening, thereby producing additional mechanical work.

The known reaction turbines have the drawback: the maximum mechanical energy for the turbine cannot be obtained from its rotor, since the torque generated in the rotor during the outflow of the working medium from its channels is limited by the discharge pressure of the environment.

Two-phase reaction turbines for obtaining mechanical energy are known, which comprise supplying a working medium into a channel of a rotor of the turbine and accelerating the working medium during outflow from the channel in one direction along a circumference perpendicular to the radius of the rotor, and providing rotation of the rotor.

A disadvantage of this known method is that the amount of mechanical energy obtained is insufficient, since during the momentary outflow of the working medium through the four channels of the rotor and the working medium supplied into the space formed by the casing in the form of a bladed turbine and through the open turbine in the casing, the working medium located between the blades is discharged, "knocked over" (out) "at the moment of flow contact with the channels of the rotor, and is thereby accelerated to the speed of the flow from the rotor channels, wherein a part of the energy of the flow is used. When flowing out through openings in the housing in the form of a radial vane turbine, there is a loss in the acceleration of the working medium in the radial vanes due to centrifugal forces. Furthermore, there are ventilation losses during the circulation of the working medium between the blades due to the outflow through the openings in the housing. Furthermore, the working medium flows out of the rotating housing in the form of a radial blade turbine at a speed which is significantly different from the rotational speed of the housing, which leads to energy losses.

There is also known a jet reaction turbine with a working wheel formed as a tube with closed ends, which is connected coaxially with a shaft, arranged with the possibility of rotation, wherein at least one pair of pipes with open ends are fixed radially on opposite sides on the tube, a housing is arranged with the possibility of rotation and around the wheel, an outer casing surrounds the wheel and the housing and has an opening for arranging the shaft, and nozzles for supplying and discharging the working medium. At least one pair of tubes having open ends are secured to the housing on opposite sides. The housing and the running wheel are arranged on the same axis.

A disadvantage of this known turbine is that it fixedly connects the housing and the running wheel arranged on a single shaft and rotates the running wheel and the housing in one direction, which provides that mechanical energy is obtained from only one housing, while the conduits of the running wheel throttle the working medium supply pressure only through elements of the turbine, which results in useless energy losses and low turbine efficiency.

Radial turbines with two shafts are known, which have a Segner (Segner) wheel formed as a tube with a closed end connected coaxially with the shaft and arranged with the possibility of rotation, at least one pair of open ends fixed radially on the tube on opposite sides and with bends on opposite sides of its axis, wherein the axis of the bent open ends of the tube is perpendicular to a plane extending through the axis of the pair of tubes and the axis of the tube, wherein walls of the tube openings corresponding to the tubes are provided, a housing connected coaxially with the shafts and arranged with the possibility of rotation and surrounding the Segner wheel, a casing surrounding the Segner wheel and an opening with the tube arranged with the Segner wheel and the shaft of the Segner wheel and the housing, and a nozzle for letting out a working medium. The housing is formed as a blade turbine.

A disadvantage of this known turbine is that in the casing formed as a bladed turbine, the blades are fixed to the disc along the turbine ends, which increases the centrifugal load on the blades due to the additional moment, and the assembly of the fixed blades cannot withstand high loads, which requires a reduction in the peripheral speed of the bladed turbine and a reduction in the efficiency of the bladed turbine. In order to pass between the vanes, the working medium fluid from the nozzles of the rotor must be directed at the vanes at an angle determined by the shape of the vanes and the shape of the flow from the nozzles. In the known turbine, the flow of working medium from the nozzles is supplied onto the blades at different angles, which on average leads to an increased angle which is acceptable for turbines with individual nozzle arrangements and to a reduced efficiency.

The use of a hollow rotor (segmenter) leads to friction losses due to the generation of a circulation of the working medium in the hollow of the rotor, which is entrained by the viscosity on the walls and the counter-flow (or in other words, the formation of a pair of rotations) in the middle part of the hollow of the rotor (segmenter). Therefore, the power taken from the rotor having the hollow portion is lost. As the working medium is supplied to the casing (bladed turbine) section from the four nozzles of the rotor (segmenter wheel) rotating in opposite directions, the working medium, at a moment of contact with the flow coming from the nozzles of the rotor, located between the blades at low pressure, is expelled, is "knocked down", is accelerated to the velocity of the flow supplied from the nozzles of the rotor, for which a part of the energy of the flow is used.

In the casing (blade turbine), there is an acceleration loss of the working medium in the radial blades due to centrifugal force. Furthermore, ventilation losses (loss for ventilation) occur as a result of the circulating or working medium between the blades during the outflow through the opening in the housing. In addition, from the rotating housing in the form of a bladed turbine, the working medium flows out at a speed that is significantly different from the speed of rotation of the housing, which leads to energy losses.

The known turbines also have a complex structure and complex techniques for their manufacture, due to the use of the blade turbine as a casing.

Methods are known for obtaining mechanical energy from a turbine, which method comprises supplying a working medium into a channel of a rotor of the turbine, accelerating the working medium as it flows out of the channel in one direction circumferentially and usually to the radius of the rotor in order to rotate the rotor, supplying working fluid from the rotor channel into a space created in a housing above the rotor, wherein the working fluid, when flowing out through an opening of the housing, interacts with the housing by friction in order to accelerate in one direction and rotate the housing, forming a space in the housing which is closed in the direction of the outlet opening of the rotor channel and which extends along a circumferential radius, and accelerating the working fluid flowing out circumferentially through the opening of the housing and usually to the radius of the housing in the opposite direction to the direction flowing out from the rotor.

A disadvantage of this known method is that the amount of mechanical energy obtained is insufficient, since the nozzle is not of the transonic type and does not provide additional thrust.

While the prior art systems described above are suitable for their intended purposes, there is still a need for improvements in the collection of thermal energy from liquids while improving the efficiency of heat collection and stable operation of the system over a wide range of operating parameters, and while the prior art hot water and condensate collection systems are suitable for their intended purposes, there is still a need for improvements, particularly systems that provide improved overall cycle thermal efficiency.

Disclosure of Invention

Embodiments of the invention include transonic two-phase reaction turbines for use with low and high temperature flowing media. The turbine includes at least two wheels configured to rotate in opposite directions, at least one of the at least two wheels being equipped with one or more kinetic energy harvesters.

Embodiments of the invention include a transonic two-phase reaction turbine having at least one rotor with a plurality of kinetic energy harvesters. Each kinetic energy collector is arranged and configured to receive the first heat carrier or carriers under pressure into a first nozzle and to receive the second heat carrier into a second nozzle, the second heat carrier being cooler than the first heat carrier, the second nozzle being arranged downstream of the first nozzle at a distance defined at least partly on the basis of the pressure and temperature, flow of the heat carrier or carriers. Each kinetic energy collector includes a mixing chamber between a first nozzle and a second nozzle, the mixing chamber configured to mix a first heat carrier and a second heat carrier to produce a two-phase mixture, the second nozzle positioned at a defined distance from the first nozzle to produce an elevated discharge thrust. Each mixing chamber is configured to cause the heat carrier pressure of the two-phase mixture to decrease and decelerate to a velocity at which the two-phase mixture, or at least one of the first heat carrier or the second heat carrier or both, boils into a homogeneous two-phase medium with small bubbles, the two-phase medium being a highly compressible medium and having a sonic condition with a mach number greater than 1. Each second nozzle is configured to focus and compress a two-phase flow of media, thereby collapsing small bubbles and changing the two-phase mixture into an incompressible single-phase flow of media with increased motive thrust. Each kinetic energy harvester further comprises a discharge portion arranged downstream of the second nozzle, each discharge portion being arranged and configured to discharge a single-phase flowing medium with increased kinetic thrust to generate a reaction pressure higher than the input pressure of both the first heat carrier and the second heat carrier for driving the rotor in a rotating manner, wherein the result is that each kinetic energy harvester generates thermal energy and kinetic energy.

These and other advantages and features will become more apparent from the following description taken in conjunction with the accompanying drawings.

Drawings

The subject matter which is regarded as the invention is particularly pointed out and distinctly claimed in the claims at the conclusion of the specification. The foregoing and other features and advantages of the invention are apparent from the following detailed description taken in conjunction with the accompanying drawings in which:

FIG. 1 is a graph showing the relationship between the speed of sound and the volume ratio of gas to liquid;

FIG. 2 is a schematic diagram of a Fisonic-type apparatus according to an embodiment of the present invention;

FIG. 3 is a schematic diagram of a system incorporating the apparatus of FIG. 2;

fig. 4 to 16 are schematic diagrams of further embodiments of a fisheric type device according to further embodiments of the present invention;

fig. 17 is a schematic diagram of a cogeneration system using the Fisonic type device of fig. 1 to 16;

figures 18 to 20 are schematic diagrams of a heat pump system using the Fisonic type apparatus of figures 1 to 16;

FIG. 21 is a schematic diagram depicting a transonic two-phase reaction turbine and heat exchanger in single-line flow diagram form, in accordance with an embodiment of the present invention;

FIG. 22 is a graph of a Rankine cycle according to an embodiment of the present invention; and

fig. 23-32 depict an alternative embodiment of a direct drive heat turbine generator according to an embodiment of the present invention.

Fig. 33A, 33B, and 33C show various design configurations of the turbine.

FIG. 34 depicts various heat sources supplied to the turbine and also depicts the end user: electrical, heating and air conditioning systems.

FIG. 35 depicts an indirect hot water system supplying steam via a two-phase nozzle, a deaerator, a process control pump, and a plate and frame heat exchanger.

The detailed description explains embodiments of the invention, together with advantages and features, by way of example with reference to the drawings.

Detailed Description

Embodiments of the present invention provide supersonic kinetic energy collectors, heat exchangers, mixers, dosers (donators), homogenizers, pasteurizers, de-superheaters, pumps, flow meters/energy meters, emulsifiers, propellers, expanders, and super condensate reclaimers (referred to herein as kinetic energy collectors, or KEH). Embodiments of the present invention generate kinetic energy and thermal energy capture and conditions that significantly reduce thermal energy and pumping energy consumption by using a KEH as described below. Embodiments of the present invention provide a KEH that converts kinetic energy of a working fluid provided by a variable speed pump into thermal energy and pumping energy and provides reliable, stable, and cavitation-free operation of the system. This provides the advantage of: the energy consumption of existing pumps and conventional thermal energy supplies is significantly reduced. Embodiments of the present invention may also be equipped with a degasser (deaerator) that thoroughly removes the incompressible gas from the liquid and substantially improves thermal energy collection. The KEH may also operate without any external pump, as long as fluid is present in the reactant mixing chamber and there is a heat gain or delta pressure, the KEH will begin to operate and will pump the fluid.

The performance of the KEH embodiments is based on the properties of two-phase flow, above all their increased compressibility. To increase the effectiveness and thermal energy collection rate of the KEH, the cold liquid is initially preheated in the boiler by district heating, solar energy, geothermal energy, wind, biomass, fossil, nuclear, waste or chemical energy, and pumped (at plant start-up) into the KEH. In KEH, a single phase liquid stream under subsonic conditions is converted into a uniform two-phase stream (plasma) which is passed into a supersonic stream containing a plurality of microscopic vapor bubbles; then collapse occurs while the vapor mixture in the supersonic two-phase flow, resulting in the transformation of the two-phase flow into a single-phase flow, providing additional thermal energy and some pumping power. The capabilities and versatility of the KEH allow the capabilities of the KEH to be configured to meet the needs of the end user to meet a particular application.

An embodiment of the KEH consists of a diffuser equipped with geometrically shaped guide ribs. The diffuser is connected to a ring equipped with a plurality of tubes having spiral ribs on the inner surface. The ribs generate vortices, resulting in a centrifugal action that provides effective liquid turbulence. The liquid then enters the open chamber. In this chamber, the original liquid flow is injected from the discharge of the KEH into an additional liquid flow that is recirculated in the concentric outer pipe. The mixed stream is further discharged to a coaxial nozzle located at the entrance of the Laval (Laval) nozzle. After the laval nozzle, the liquid pressure is reduced to a value not higher than the saturated vapor pressure corresponding to the liquid temperature. Under these conditions, a plurality of vapor bubbles are formed in the liquid. The length of the laval nozzle is a predetermined length.

At a predetermined distance from the laval nozzle, the liquid enters the geometry nozzle, after which a counter-pressure is applied, causing pressure fluctuations to occur in which the vapor component of the two-phase flow collapses. During the pressure fluctuations, a range of oscillations are generated, promoting the collapse of the newly formed small vapor bubbles, which in turn generates thermal energy and increases the temperature of the liquid and the thrust of the liquid. At this point, a portion of the liquid is separated from the main flow and recirculated back to the mixing chamber at the inlet of the KEH. The main liquid flow moves a predetermined distance and then enters a geometric ring/screen where additional thermal energy is collected. The liquid then enters a conical discharge from which the liquid, having an elevated temperature, is discharged into a pipe system. The recirculation of the partial stream within the KEH allows to provide a reliable and stable operation mode of the system under a wide range of system parameters (flow rate, temperature and pressure).

The heated liquid is delivered to a hot user. The cooled liquid stream may be recirculated from the user back to the boiler or other heat input source. The return liquid may also pass through a degasser in which the liquid is degassed deeply. Removal of incompressible gas in the deaerator improves the energy collection process. In the repeated recirculation cycles, the main heat input and pumping power is provided by the KEH and the heat input of the boiler and the pumping power of the pump are significantly reduced. When liquid is not returned from the customer, make-up liquid is provided to the KEH.

The dependence of the jump pressure (jump pressure) P2 on the pressure inside the device (Pbj) before the jump (jump) is described by the following equation:

(3)P₂＝k P_bjM²…

in transonic or supersonic flow, a uniform two-phase flow is achieved by reducing the sonic velocity, which permits a maximum number equal to or greater than one (M ≧ 1) to be achieved at low flow rates.

The operational balance of KEH is described by the following equation:

wherein:

k＝Cp/Cv；

cp is constant pressure specific heat; cv is constant volume specific heat; w, i, d — subscripts denoting the following parameters of the working, injection and discharge streams: p is pressure and V is specific volume; and u is the injection coefficient, equal to the ratio of the injected flow rate and the operating flow rate.

The specific characteristics of the KEH are closely related to the geometry of the mixing chamber. The discharge pressure (Pd) after KEH is represented by the following formula:

wherein: t is_w1＝P_i/P_w；_w1The section of the working nozzle exhaust; f. of₃The section of the mixing chamber exhaust; k₁Work flow velocity coefficient;a diffusive flow velocity coefficient; t is_wc＝P_c/P_wThe ratio of the pressure in the critical section of the working nozzle to the working pressure; lambda [ alpha ]_w1The ratio of the velocity of the workflow at adiabatic flow to the critical velocity; f. of_wcThe section of the critical section of the working nozzle; and u is the injection coefficient.

The relationship between pressure at the inlet (P2) and the injection coefficient in the mixing chamber is determined by the following equation:

the energy conservation equation for a medium with any compressibility is:

(7)dq＝(K/k-1)P du+1/(k–1)*u*dP+dqmp

for incompressible fluid moving in an adiabatic tunnel (k → ∞, dv ═ 0), the only source of heat is friction. Incompressible fluids cannot be used as a working medium for converting thermal energy into mechanical work. The situation is different when applying equation (7) to the cross section of the flow at the pressure surge boundary, where the highly compressible two-phase mixture of the mist structure is located on one side, while the single-phase liquid with small bubble vapor (gas) on the other side of the pressure surge section is located.

The conditions for thermal equilibrium in the pressure surge mode are:

(8)ρ_1d(1-β)*Δq＝ρ_g*β*r

(9)Δq＝(ρ_g/ρ_1g)*r*(M²-1)

wherein: r is latent heat of phase change. Several conclusions can be drawn from the analysis of equation (9). First, At M <1, Δ q <0 are well known processes of liquid evaporative cooling processes. Second, Δ M ═ 1, Δ q ═ 0 — are The phenomena Of degradation Of turbulence described in references 3 and 4, respectively, Vulis, l.a, "Gas dynamics Of Gas flow" (gosensenergozdat M, l.1950), for internal problems Of Gas moving close to The outlet portion Of The cylindrical channel at near critical velocity, reference 4 is Fisenko, v.v. and Sychikov, v.i. "compressive influence On aerodynamics Of Two-Phase flow (On The compressive efficiency effect On hydrogen dynamics Of Two-Phase flow", 1977, volume 32, No.6, 1977, v.32), for problems Of external cylinders around The flow velocity ". For homogeneous two-phase mixtures, The problem is solved In reference 5, which is "about hydraulic Resistance In The Supersonic region Of fluids" (on The hydralic Resistance In The Supersonic Zone Of Flow) "by Gukhman, a.a., Gandelsman, a.f., and Naurits, l.n., encyclophane No. 7 Of 1957. Finally, M >1, Δ q >0 is a phenomenon addressed by U.Potapov in reference 6 under the influence of certain internal geometries on the flow, reference 6 being "Vortex Energy" by Potapov, U.S./Fominskii, L.P.h. and Potapov, S.U., which is described in www.transgasindustry.ru/books.

The maximum possible thermal energy release from the internal energy of the liquid under the controlled geometric, thermal, cost or combined influence of the fluid flow is described by the following equation:

(10)

Δq＝(ΔP/ρ_1d)*(M²k-1)

wherein: Δ P — the difference between the pressure in the surge supplying the generated energy and the back pressure of the system; and ρ ld ═ the density of the liquid at the KEH outlet.

Experiments have demonstrated that by changing the internal geometry of the KEH, temperature, pressure, chemical composition, adding sound waves, electrical stimulation, tubing configuration, combination of gas and liquid, and gravity, the device parameters can be changed and enhanced and the thermal energy collected and pumping power substantially increased.

One embodiment of the KEH20 is shown in FIGS. 2 and 3. The liquid 1 is pumped and initially preheated in a device 22 such as, but not limited to, a boiler utilizing district heating, solar energy, geothermal heat, wind, biomass, fossil, waste or chemical energy. It should be understood that while the embodiments described herein refer to a linear configuration of KEH, the claimed invention should not be so limited. In some embodiments, the KEH is configured in the shape of a 360 degree annular ring, for example. After heating, liquid 1 is pumped (during start-up) into the KEH 20. The KEH20 comprises a diffuser 2 equipped with geometrically shaped guide ribs 3. The diffuser is connected to a ring 4 equipped with a plurality of tubes 5 having helical ribs on the inner surface. The ribs are configured to generate a swirling flow that induces a centrifugal effect to provide turbulent flow of the liquid. The liquid then enters the open chamber 6. The length of the mixing chamber may vary depending on the end use application. In the chamber 6, a part of the original liquid stream 1 is injected as an additional liquid stream 7. The liquid stream 7 is recirculated in the concentric outer pipe 8 through the outlet of the nozzle 11 of the KEH 20.

The mixed stream is further discharged into a first laval nozzle 9 compressing the single phase liquid stream 7. In one embodiment, one or more pressure sensors 36 are coupled to the first laval nozzle 9. The pressure sensor 36 is configured to provide a signal indicative of the pressure in the first laval nozzle 9 to the liquid flow metering device 38. The liquid stream 7 is discharged into a second laval nozzle 10. At a predetermined distance from the second laval nozzle 10, the fluid enters the nozzle 11. In one embodiment, the pressure of the single-phase liquid fluid after passing through the laval nozzle is reduced to a value no higher than the saturation vapor pressure corresponding to the liquid temperature. Under these conditions, a plurality of vapor bubbles are formed in the liquid. After passing through the nozzle 11, part of the liquid flow is separated and recycled to the chamber 6 through the concentric tube 8. It has been found that the recirculation of the partial stream inside the KEH20 allows to provide a reliable and stable operation mode of the system at a wide range of system parameters (flow rate, temperature and pressure).

In one embodiment, nozzle 11 provides a braking effect on the two-phase flow and generates a backpressure that causes the occurrence of pressure fluctuations in which the vapor component of the two-phase flow collapses and converts the two-phase flow to a single-phase flow. During the pressure fluctuations, a range of oscillations are generated, promoting the collapse of microscopic steam bubbles, which in turn collects thermal energy and increases the temperature of the liquid and the thrust of the liquid.

The main liquid flow moves a predetermined distance and enters the ring/screen 12. After that, the main liquid flow enters a conical discharge section 13 equipped with ribs 14, from which the liquid of raised temperature and thrust is discharged into the piping system. In one embodiment, the piping system includes a conduit that returns a portion of the discharge stream from the KEH20 to the pumping device 34. In the exemplary embodiment, pumping device 34 is a water turbine pump or a Fisonic jet pump.

It should be understood that the KEH20 may include additional nozzles or inputs for supplying additional liquids and gases for mixing with the main liquid stream and producing a homogeneous mixture and emulsion.

In one embodiment, the piping 15 may be equipped with a flash separator 24 in which heated water is flashed and steam is separated and supplied to an end use application 26 such as a building steam heating system. The separator is connected to the KEH20, reducing the pressure in the separator and providing water flash conditions.

The heated liquid or vapor is then delivered to the end-use application 26. Once the thermal energy is extracted from the heated liquid or vapor in the end-use application, the cooled liquid or condensate stream is recycled back to the boiler 22 or other heat input source. The return recycle line may also be connected to a degasser 28 where the liquid is deeply degassed to provide non-compressible gas removal, make-up and liquid expansion functions. In one embodiment, the deaerator also serves as an expansion device. In embodiments where cooled liquid is not returned from the end-user application 26, make-up water 30 is supplied to the system 32. The heat input and pumping power provided by the KEH20 and the heat input of the boiler during repeated recirculation cycles significantly reduces the requirements of the pump 34 of the system 32.

In one embodiment, the KEH utilizes interparticle forces (kinetic energy of a two-phase and multi-phase medium) and is used for mixing, temperature elevation, and generation of liquid and gas thrust and vacuum. The system may include a heat input device in the form of a boiler, district heating, solar, geothermal, wind, biomass, fossil, waste or chemical energy, a pump (for initial start-up) connected to the KEH that creates conditions for energy collection and pushes the heated liquid to a piping system connected to the consumer in an open or closed loop cycle of liquid medium, and which may include a degasser. Technical effects include constructing a KEH for a particular operating range. In one embodiment, the thermal energy collection temperature range should be between 110 ℃ and 250 ℃. The KEH is suitable for use in various industries, traffic, irrigation, disinfection, fire suppression, water/oil separation, mixing, cooking, heating, cooling, and low-quality energy utilization.

Experiments have demonstrated that by changing the internal geometry of the KEH, temperature, pressure, chemical composition, addition of sound waves, electrical stimulation, tubing configuration, combination of gas and liquid, and gravity, the device parameters can be changed and enhanced and the kinetic and thermal energy harvested and the pumping power can be significantly increased.

Fig. 4 to 17 show different embodiments of the KEH. The KEH20 of FIG. 4 illustrates an embodiment in which the KEH20 is implemented as a two-phase or multiphase thermodynamic amplifier. In this embodiment, the KEH20 has a single Laval nozzle 9 and a brake nozzle 11. In the embodiment of fig. 4, there are no concentric conduits for recirculating a portion of the fluid flow. Instead, the conduit 40 injects a fluid flow, such as a cold liquid heat carrier, between the inlet of the laval nozzle 9 and the inlet of the nozzle 11.

Referring now to fig. 5, an embodiment is shown in which the KEH20 is implemented as a supersonic kinetic amplifier. In this embodiment, a single laval nozzle 9 is arranged downstream of the diffuser 2. The liquid exiting the laval nozzle 9 mixes with the recirculating liquid from the concentric conduit 8 and enters the brake nozzle 11. Upon exiting the nozzle 11, the liquid stream is recirculated through the concentric conduit 11, while the remainder is discharged through the conical discharge section 13.

Referring now to fig. 6, an embodiment is shown in which the FD 20 is implemented as a multi-stage high power amplifier. In this embodiment, the liquid flow 1 enters the chamber 6 via the diffuser 2. At a predetermined distance downstream of the diffuser 2, the outlet of the concentric conduit 8 causes the recirculated liquid to flow into the chamber 6, thereby causing the two fluid streams to mix. The mixed stream then enters a single laval nozzle 9 and a brake nozzle 11. The inlet of the concentric conduit 8 is arranged at the outlet of the nozzle 11 so that a part of the liquid flow is recirculated, while the rest of the flow is discharged via the discharge section of the discharge portion 13.

Figure 7 shows the KEH20 implemented as a multiphase thermodynamic amplifier for hybrid and multi-stream applications. The liquid stream 1 is received by the diffuser 2 and passed into the chamber 6 where the liquid stream 1 is mixed with the recirculating liquid from the concentric conduit 8. The mixed liquid flows into the laval nozzle 9. The second liquid stream is injected through conduit 40. The second liquid is injected between the inlet and the outlet of the laval nozzle 9. The combined liquid flow enters the brake nozzle 11, the inlet of the concentric conduit 8 being arranged at the outlet of the nozzle 11 to cause a recirculation flow of a portion of the liquid flow. The remainder of the mixed fluid stream is discharged via discharge section 13.

Fig. 8 shows the KEH20 implemented as a super power thruster. In this embodiment, liquid 1 is received in diffuser 2 and enters chamber 6 through a plurality of nozzles 42. The liquid passes through a laval nozzle 9 and combines with the recirculating liquid from the concentric conduit 8. The concentric conduit injects the recirculating liquid outside the laval nozzle 9 upstream of the discharge outlet 44. The liquid from the laval nozzle 9 and the recirculated liquid mix at the inlet of the brake nozzle 11. In this embodiment, the discharge outlet 44 and the inlet of the nozzle 11 are substantially co-located. The inlet of the concentric conduit 8 is arranged at the discharge of the nozzle 11 to recirculate a part of the fluid flow. The remainder of the mixed fluid stream is discharged via discharge section 13.

Fig. 9 shows the KEH20 implemented as a multi-input energy harvester. In this embodiment, the liquid 1 passes through the diffuser 2 and is guided by the ribs 3 into a ring 4 having a plurality of tubes 5. The liquid enters the chamber 6 through the pipe 5. Conduit 40 injects a second liquid stream into chamber 6, as well as the recycled liquid from concentric conduit 8. The combined liquid stream enters a laval nozzle 9. A third liquid stream is injected from the conduit 46 such that the liquid 1, the recirculated liquid, the second liquid stream, and the third liquid stream mix at the discharge port 44 and enter the brake nozzle 11. In this embodiment, the inlet and discharge 44 of the nozzle 11 are co-located. The inlet of the concentric conduit 8 is arranged at the discharge of the nozzle 11 to cause recirculation of a portion of the fluid flow. The remainder of the mixed fluid stream is discharged via discharge section 13.

Figure 10 shows the KEH20 implemented as a two-stage thermal energy collector with external feed. In this embodiment, liquid 1 is received into the chamber 6 through the diffuser 2. The liquid then flows through a laval nozzle 9. The external feed conduit 40 injects a second fluid stream externally of the laval nozzle 9 upstream of the discharge outlet 44. The liquid 1 and the second fluid flow mix at the discharge port 44 and enter the brake nozzle 11. At the discharge of the nozzle 11, a ring 48 having a plurality of tubes receives the liquid stream, thereby allowing the liquid stream to be discharged through the discharge section 13.

Fig. 11 shows the KEH20 as implemented as a lower quality energy utilisation. In this embodiment, the liquid 1 is received via the diffuser 2 into the inlet 54 of the laval nozzle 9. The second fluid stream is injected coaxially with the liquid 1 at the inlet 54. In this embodiment, the inlet 54 is substantially co-located with the outlet of the diffuser 2. The combined fluid stream flows through the laval nozzle 9 and into the brake nozzle 11. The inlet of the nozzle 11 is substantially co-located with the outlet 44. The liquid stream exits the KEH20 via the discharge section 13.

Fig. 12 shows the KEH20 implemented as a combined energy harvester and thruster. In this embodiment, the liquid 1 passes through a diffuser 2 and is guided by ribs 3 into a ring 4 having a plurality of tubes 5. The liquid enters the chamber 6 through the pipe 5. Liquid flows from the chamber 6 into the first laval nozzle. The second liquid stream is injected by a conduit 40 external to the first laval nozzle 9. The liquid 1 from the first laval nozzle 9 and the second liquid stream are mixed at the outlet 44. At a predetermined distance from the discharge opening 44, the second laval nozzle 10 receives the mixed liquid stream. The discharge port 56 of the second laval nozzle 10 is arranged substantially co-located with the inlet of the brake nozzle 11. The concentric conduit 8 injects the recirculating liquid at the discharge 56. The inlet of the concentric conduit 8 is arranged at the discharge 56 of the nozzle 11 to enable recirculation of a part of the fluid flow. The remainder of the mixed fluid stream is discharged via discharge section 13.

Fig. 13 shows the KEH20 as performed as a waste heat utilization scrubber. In this embodiment, the first liquid 1 is received via the diffuser 2 and the second liquid is received from a coaxially arranged conduit 57. The two liquid streams are directed into a ring 4 having a plurality of tubes 5, into a chamber 6. These two liquid streams are directed through mixing with the first waste heat liquid stream from conduit 40 in chamber 6. The combined mixture passes through the first set of vanes 58 into the second chamber 59 where the liquid flow is combined with the second waste heat liquid flow from conduit 46. The combination of flows is directed through the second set of vanes 60 to the discharge section 13.

Fig. 14 shows a KEH20 performed as a gas/liquid mixing device for e.g. pasteurization and homogenization. In this embodiment, the liquid 1 is received by the diffuser 2 and enters the chamber 6. Liquid flows from the chamber 6 into the laval nozzle 9. The second liquid stream is injected outside the laval nozzle 9. The liquid flowing from the laval nozzle 9 is mixed with the second liquid stream at the discharge outlet 44. The combined liquid then flows into the brake nozzle 11. The inlet of the nozzle 11 is substantially co-located with the discharge outlet 44. After passing through the nozzle 11, the combined liquid is discharged via the discharge section 13.

Figure 15 shows the KEH20 implemented as a cavitation heat expander. In this embodiment, the liquid 1 enters via a first conduit 72 having a first diameter. The flow of liquid impinges on a cavitation device 76 located in the conical inlet section 74. The liquid then flows into a second conduit 78 having a second diameter and a predetermined length. The diameter of the second conduit 78 is smaller than the diameter of the first conduit 72. After passing through the second conduit 78, the liquid enters the chamber 6 via the diffuser 2. The chamber 6 has a predetermined length and terminates in a discharge section 13.

Figure 16 shows the KEH20 operating as a thermal energy collector and amplifier. In this embodiment, the liquid 1 passes through the diffuser 2 and is guided by the ribs 3 into a ring 4 having a plurality of tubes 5. The liquid enters the chamber 6 through the pipe 5, where it mixes with the recirculating liquid from the concentric conduit 8. The mixed liquid flows from the chamber 6 into the first laval nozzle 9. The mixed liquid is discharged from the first laval nozzle 9 and flows a first predetermined distance before entering the second laval nozzle 10. The mixed liquid then flows a second predetermined distance before entering the brake nozzle 11. The inlet of the concentric conduit 8 is arranged at the discharge of the nozzle 11 so that a part of the fluid flow is recirculated. At the discharge of the nozzle 11, a ring 48 having a plurality of tubes receives the liquid stream, thereby allowing the liquid stream to be discharged through the discharge section 13. In this embodiment, the discharge section 13 includes ribs 62 that direct the flow.

Referring now to fig. 17, an exemplary embodiment of a system 100 using one or more of the KEH20 embodiments described herein is shown. The system 100 is a combined heat and power system that provides both thermal and electrical energy to an application, such as a manufacturing company or commercial office building.

The aqueous emulsion portion 102 mixes fuel from the fuel tank 100 with steam in the transonic emulsification device 112. The emulsified fuel is delivered to the boiler 114 by a pump 116. The fuel is combusted to produce steam. The vapor is transferred by pump 118 to heat utilization and gas purification transonic apparatus 120. The apparatus 120 combines the high temperature flue gases from the boilers 114 to produce a high pressure, high temperature steam mixture at its output 122. The nature of the output 122 is suitable for use in a water vapor transonic turbine engine 124. The engine 124 rotates a generator 126 to produce electrical power. It should be appreciated that the conditions of the steam mixture at the outlet of the engine 124 may be greater than Mach 1(Mach 1).

An output 128 of the engine 124 delivers the vapor mixture to a transonic condenser 128. Within the condenser 128, the two-phase steam from the engine 124 is accelerated, after which mixing of the steam and condensate is achieved to form a two-phase mixture, wherein the two-phase mixture stream is transferred to the supersonic stream. Pressure changes are effected in a two-phase supersonic flow, during which a two-phase flow is transferred into a single-phase liquid subsonic flow by collapse of vapor bubbles and by intense vapor condensation. At the same time, the condensate is heated by the intense condensation of steam in the condensate and the collapse of the steam bubbles during the pressure change to form a single phase high temperature liquid. In one embodiment, the liquid is additionally heated within the condenser 128 by adding a deceleration stage.

The single-phase high temperature subsonic liquid flows into a heat exchanger 130 having a gas/water capacity. The heat exchanger transfers thermal energy from the single-phase liquid to a heat transfer medium, such as water. The heat transfer medium can then be used for space heating, domestic hot water or process heat, for example. The cooled single phase liquid passes from the heat exchanger to a degasser 132, such as a cyclone degasser, which separates entrained air and gas from the liquid. The separated gas is filtered and vented to the atmosphere.

Liquid is removed from deaerator 132 and transferred to condensate section 108 via pump 134. In the condensate section 108, the liquid stream passes through a transonic chemical reactor apparatus 136 and into a vortex reactor 138. The condensed liquid may be filtered using a manifolded filter apparatus 140 before passing back to the boiler 114 for reuse.

Referring now to fig. 18-20, an exemplary embodiment of a system 200 using a KEH202 having a heat pump 204, such as for heating a residence 206, is shown. In the exemplary embodiment, system 200 is coupled to a geothermally closed loop surface water system 208. It should be understood that while the embodiments herein relate to geothermal systems, the claimed invention should not be so limited. The system includes a geothermal portion 208 that receives a heat transfer medium or coolant from the heat pump 204. The coolant is discharged from the geothermal portion 208 and transferred into the KEH202 via a pump 210. The temperature and pressure of the coolant is increased by means of the KEH202, as described herein above. The coolant is discharged from the KEH202 into the conduit 212. An expansion tank 214 is coupled to the conduit 212. The coolant enters the heat pump 204. When in the cooling mode of operation (fig. 19), the heat pump 204 transfers heat to the coolant via the heat exchanger 216. The coolant is then transferred to the geothermal portion 208 where the thermal energy is transferred to the surface. When in the heating mode of operation (fig. 20), the coolant transfers heat to the heat pump 204 via the heat exchanger 216. The cooled coolant is then transferred to the geothermal portion 208 where the coolant is heated by the surface.

According to another embodiment of the invention, a KEH coupled to one or more heat generating devices is provided. A first apparatus is provided having a plurality of inputs including a first input and a second input fluidly coupled to a heat generating device. A variable speed first pump is fluidly coupled to supply fluid from the heat generating apparatus to the first apparatus. A degasser is fluidly coupled to receive fluid from the first device. In one embodiment, the apparatus includes a second pump fluidly coupled to the first device. A second device is fluidly coupled to the inlet of the second pump. A third device is fluidly coupled to the output of the second pump. The KEH improves the flow of fluid into the pump impeller, thereby reducing electrical consumption and increasing fluid volume.

According to another embodiment of the present invention, a KEH is provided that includes a diffuser fluidly coupled to a first input. The diffuser has guide ribs, wherein the pump flows liquid into the diffuser, wherein the diffuser is connected to a ring having a plurality of tubes with spiral ribs on the inner surface. The ribs generate a swirling flow resulting in a centrifugal effect that causes the liquid to create a turbulent flow, wherein the first device comprises an open chamber adjacent the ring. The plurality of inputs are arranged to inject a further liquid recirculation flow in the concentric outer tube of the discharge portion of the first device.

According to another embodiment of the invention, a KEH is provided in which the fluid mixed after passing through the opening chamber is further discharged into a coaxial nozzle located at the inlet of the laval nozzle. The single phase liquid is compressed in a laval nozzle. The pressure of the single-phase liquid stream after passing through the laval nozzle is reduced to a value no higher than the saturation vapor pressure corresponding to the liquid temperature to form a plurality of vapor bubbles within the liquid. The apparatus includes a brake nozzle adjacent to the laval nozzle. The brake nozzle is configured to exert a braking action on the two-phase flow and to generate a back pressure that causes the occurrence of pressure fluctuations, wherein the collapse of the vapor composition of the two-phase flow and the transformation of the two-phase flow into a single-phase flow, wherein during the pressure fluctuations a range of oscillations are generated, thereby promoting the collapse of tiny vapor bubbles, which increases the liquid temperature and liquid thrust.

According to another embodiment of the invention, a KEH is provided in which a portion of the liquid is separated downstream of the brake nozzle and recirculated back to the inlet of the chamber. The main discharge liquid flow moves a predetermined distance and then enters the ring/screen section whereby the temperature of the liquid further increases and wherein the main discharge liquid flow moves a predetermined distance and then enters the conical discharge section. In one embodiment, the laval nozzle includes a pressure sensor connected to an external liquid flow metering device.

According to another embodiment of the invention, a KEH is provided in which the distance between the outlet of the laval nozzle and the discharge section has a predetermined size. The inlet of the laval nozzle is provided with perforations. A portion of the fluid discharged from the discharge section is pumped back into the hydro turbine pump, which provides the fluid into the pumping apparatus. In one embodiment, the first apparatus further comprises additional nozzles for supplying additional liquids and gases that mix with the main liquid stream and produce a homogeneous mixture and emulsion. In another embodiment, the flash separator is fluidly coupled to the discharge stream, and wherein the first apparatus is configured in the shape of a 360 degree annular ring.

According to another embodiment of the present invention, a method of operating a KEH is provided. The method comprises feeding at least one liquid heat carrier under pressure into a nozzle, feeding a cold liquid heat carrier, and mixing the liquid heat carrier and the cold liquid heat carrier. Wherein one of the two transformations is performed with a liquid flow of a liquid heat carrier mixture. The first transition consists in accelerating the heat carrier mixture to the speed at which the heat carrier mixture or at least one of the heat carriers in the mixture boils, and in forming a two-phase flow, in which the latter is transitioned to a condition in which the mach number is greater than 1, then in changing the pressure in the latter of the two-phase flow to a subsonic liquid flow of the heat carrier mixture, and in carrying out the heating of the liquid of the heat carrier mixture during the pressure change. The second transformation consists in accelerating the flow of the heat carrier mixture to the speed at which at least one of the heat carrier mixture or the heat carriers of the mixture boils and forms a two-phase flow, in which the latter is transformed to conditions with a mach number equal to 1, then in decelerating the two-phase flow, so that the fluid is transformed into a flow of heat carrier mixture with steam bubbles, and moreover, by the transformation of this flow, the flow of heat carrier mixture is heated; the two above-mentioned transformations of the liquid stream of the heat carrier mixture, which is fed to the consumer under the pressure obtained in the spraying device, are then carried out in any order.

According to another embodiment of the invention, the KEH may be used to emulsify, homogenize, heat, pump and modify its rheological properties, prevent the formation of space volume structures at temperatures below the crystallization point of paraffins, and the structure of various hydrocarbons. This application also allows the breakdown of the intermolecular bonds of bitumen/paraffin wax that lead to an abnormal viscosity. KEH also reduces the concentration of high molecular compounds, mainly asphaltenes, which are the centers of supramolecular aggregates.

According to another embodiment of the invention, the KEH may be used for gas/hydrocarbon Enhanced Oil Recovery (EOR), increasing gas/oil production, increasing liquid and gas separation and production, while heating, breaking up oil particles, encapsulating water with a layer of oil, and preventing concentration of pools of water that cause oil line breaks. The application also allows the generation of intense cavitation shock waves and pressures to drive the sludge oil sacs to be pumped or to evacuate the oil/gas from the well. This application also allows paraffin decomposition and heavy crude oil formation.

According to another embodiment of the present invention, KEH may be used to enhance the production of cellulose and algae based biofuels and other organic based products by micronization caused by controlled internal shock waves and shear energy generated by KEH for more thorough and energy efficient in-line cooking, including activation of starch fermentation at lower temperatures and the need to use less additives.

According to another embodiment of the invention, the KEH may be used in applications that use excess heat in the nuclear reactor cavity to maintain recirculation of coolant until the reactor temperature drops to a safe level and prevent melting of the reactor rods. KEH will work as long as there is Δ T or Δ P. The KEH has no moving parts and requires no power. The KEH will use any water source to circulate the cooling fluid.

According to another embodiment of the invention, a method of operating a steam district heating system is provided, whereby steam is introduced into a steam/water heat exchanger and hot water is pumped through a user's liquid circulation system. The KEH replaces the conventional heat exchanger and electrically driven pump, saving energy and the requirement to suppress condensate prior to discharge. The KEH is used to replace the conventional steam/water heater exchanger of a domestic hot water supply, with a more efficient autonomous water/hot water supply circuit. The KEH recovers the exhaust condensate from the steam heated building and upgrades the condensate to usable steam with a small amount of steam for circulation in the building heating system. The KEH recovers the discharged condensed water or suppresses the waste steam with cold water and is disposed of as waste, recycled to the building for use in hot water systems or used as grey water for various purposes.

According to another embodiment of the present invention, a method of heating water using KEH to operate a hot water tank, swimming pool or any large volume of water while destroying any microbial or bacterial components in the water eliminates the need for large amounts of antimicrobial additives, such as chlorine.

According to another embodiment of the present invention, a method for simultaneous pasteurization and homogenization of milk dairy products and other liquid or semi-liquid consumables by using KEH in a single pass operation is provided.

According to another embodiment of the present invention, a method is provided for enhancing beer production, system maintenance and energy savings in wort processing by controlled internal shock wave and shear energy induced micronization generated by KEH for more thorough mixing, in-line cooking transient energy efficiency, activating starch fermentation at lower temperatures, requiring the use of less additives and antimicrobial action for post-operational system cleaning.

According to another embodiment of the present invention, a method is provided for enhancing industrial cleaning, washing, decontamination, fire protection and pretreatment preparation using high pressure atomization, sterile mixing, atomization and precise control capabilities of KEH.

According to another embodiment of the invention, a method of increasing fuel efficiency of an engine (including diesel and turbine) by improving the mixture, input pressure and ratio of air, fuel, water or additives for enhancing combustion and reducing emissions using KEH.

Referring now to FIG. 21, the operation of an embodiment of the present invention is shown in single line flow diagram form. The condensate, waste hot water, waste steam, and/or gas 420 (temperature from 40F to 540F) is passed through an optional initial KEH422 (similar to the KEH20 described above) which is used to increase the pressure and temperature of the water or gas, resulting in a single phase flow medium at the discharge end. In one embodiment, the KEH422 may be the same as the FD device described in commonly owned U.S. patent publication 2012/0248213 or commonly owned U.S. patent publication 2012/0186672, which are incorporated herein by reference in their entirety.

Following the KEH422, the single-phase or multi-phase flow medium is introduced through an inner or outer passage 424 into the center of the shaft and through the sides of one or more wheels 426 of a turbine wheel, generally referred to herein as a rotor. An example turbine wheel 426 having a two-phase flow input in accordance with an embodiment of the invention is described in more detail below with reference to fig. 23-33. Each segment of the wheel 426 is equipped with one or more KEHs 428. In embodiments utilizing the optional KEH422, the single-phase exhaust fluid flow from the KEH422 provides one of two heat carriers that are fed into the wheel 426, the second heat carrier also being fed into the wheel in the manner described in detail below in connection with FIGS. 23-33. In the final section of the KEH 428, the two-phase supersonic flow is converted to a higher pressure reaction force in the manner described above and in detail below, which causes the wheel to rotate and accelerate. Thus, high pressure media will be injected from the nozzles into the direct contact condenser 430 at a rate of 600ft/sec to 1000ft/sec, thereby generating reactive thrust and rotating the shaft with the generator 440 coupled to the shaft. The generated power may be used immediately or stored in an electrical storage device (such as a battery) 442.

The medium within the condenser 430 may then be further used, such as in a district heating and cooling system 432 or on domestic hot water 434. In one embodiment, the KEH 436 (such as the aforementioned devices disclosed in U.S. patent publication 2012/0248213 or co-owned U.S. patent publication 2012/0186672) may receive the medium and cold make-up water 438 from the condenser 430 to generate domestic hot water.

The integration of the wheel 426 and the rotating KEH 428 operating under any heat source, low grade liquid or gas of any pressure and temperature and generating electricity at high thermal efficiency advantageously provides renewable advanced clean green electricity. The system can be used for recovering waste energy of buildings, industry, solar energy and the like. The KEH is a supersonic condensing heat pump with internal geometry that mixes and accelerates steam, water or other gas and liquid, converting a small portion of the fluid heat energy into physical thrust (pump head), with the outlet pressure being higher than the pressure of the working medium at the nozzle inlet.

Embodiments of the present invention overcome the limitations of existing systems by substantially increasing the efficiency of power generation, as shown in FIG. 22, which presents a comparison of the proposed cycle with existing cycles utilizing conventional steam turbines.

Denoted as "a-b-c-d-d'" in fig. 22 is an ideal Rankine (Rankine) cycle without superheat. The position of point "b" is determined by the maximum allowable dryness of the steam.

Embodiments of the present invention overcome the limitations of existing steam turbines. It is well known that for steam turbines with modern blades, the required steam dryness should be 88% to 92%. At higher humidity, irreversible losses increase rapidly and the dynamic loads on the blades associated with unbalanced flow also increase. Thus, the turbine operates with low internal efficiency. Therefore, the expansion of the saturated steam in the steam turbine is limited by curves X and BC. In an exemplary embodiment, the expansion process starts from the lower boundary curve (corresponding to d '-b' in fig. 22). The thermodynamic cycle in which the turbine operates corresponds to the profile of d ' -b ' -c-d-d '. If the working fluid in front of the turbine is not heated to saturation temperature, the working process will correspond to line e-k-m and first the device will operate as a pure hydraulic device and after reaching the state of point 'k', as a water-steam device. If the change in heat capacity is neglected, the ideal proposed cycle in the T-S diagram is represented in the form of a right triangle c-k-m-c. Thermodynamic analysis shows that the power generation efficiency of the cycle can reach 60% to 70%.

Embodiments of the present invention allow for the generation of electricity from waste water or gas without the use of fossil fuels and the associated pollution. Large volumes of wastewater and gases from various industries currently discharging into the environment will be sources of environmental purification, renewable power generation and heat supply.

Embodiments of the present invention may also be used as a desuperheater device, combining a working stream with various waste steam streams, resulting in significant energy advantages over existing desuperheater devices.

Embodiments of the present invention may also be used as water coolers to preheat water for power plants and various industries while generating electricity.

Embodiments of the present invention may also be used as a reliable power generation device for emergency power supply or cooling in a nuclear power plant.

Embodiments of the present invention may also be used as a pump attached to a shaft using the power of the pump and having the ability to pump two-phase liquids representing most fluids used in the power generation industry, and minimizing energy losses in the condenser.

In one embodiment, the low or high temperature medium is received from (but not limited to): waste water (from cooling towers, condensers, waste gas streams from industry, and heat recovery of waste steam), steam, gases, various fluids, chemicals, particulates, or combinations thereof.

Embodiments of the present invention can be used to obtain green mechanical energy with minimal thermodynamic losses for driving generators, pumps, compressors, heat pumps and generating thermal energy, reducing the exhaust heat to the environment.

Embodiments may also be associated with primary power such as steam and water turbines, gas turbines, and reciprocating engines that generate electricity as a by-product of heating water.

In other embodiments, the engines and heat exchangers may be used for electrical, heating, cooling, pumping, metering, mixing, combustion, cleaning, hydraulic crushing of deep shale, emulsion, solar systems, environmental protection, chemical, and nuclear reactor applications for pumping and cooling.

In one embodiment, the internal molecular bonds of the working medium are broken when passing through the reactive portion in the KEH. In one embodiment, the working medium passes through the KEH to increase the medium discharge pressure and temperature. Thereafter, the medium is introduced into the center of the wheel through the internal passage or into the drum of the wheel through the seal-side nozzle connection. Each branch of the round is provided with a KEH. The wheel begins to rotate, increasing the centrifugal force of the fluid entering the wheel drum, thereby creating a higher pressure of the drum and a velocity of the KEH. The working medium pressure in the wheel branch rises, the fluid accelerates, enters a low pressure zone in the expansion portion of the KEH and boils vigorously. Thus, a supersonic single phase jet discharged from a KEH at high pressure and velocity accelerated at a rate of 600ft/sec to 1000ft/sec directly contacts the condenser, generating reactive thrust, turning a shaft or shafts. The condensed steam creates a vacuum and the casing is below atmospheric pressure, causing a reduction in frictional losses in the turbine. The turbine's wheel operates as a pump, removing water to complete the turbine cycle, or supplying heat to heat exchangers, boilers, district heating systems, and other users

In one embodiment, the mechanical energy gain is achieved with minimal thermodynamic losses by increasing the efficiency due to maximum use of multiple exhaust streams of thermal and kinetic energy of useful working media flowing from the KEH of the turbine. This embodiment may also include a housing that surrounds the wheel, is equipped with concave or other shaped vanes, and rotates by flow into the housing opening, providing additional mechanical energy. The wheel will rotate in the opposite direction due to the reaction force exerted on the wheel. The energy may be controlled by an electrical load factor applied to the two turbine wheels so that the outer wheel rotates at a lower speed than the inner wheel. To identify maximum efficiency, the main inner wheel shaft is connected to the generator rotor and the second outer wheel is connected to the generator stator.

Embodiments of the present invention further solve the problem of increased mechanical energy gain in the turbine by increasing efficiency due to minimal energy loss during the ejection of the working medium from the KEH, and also simplify the construction of the turbine. The system described may use a vertical or horizontal turbine arrangement.

Embodiments of the present invention may be further integrated with solar energy systems, heat pumps or auxiliary boilers to efficiently generate heat, domestic hot water, cooling and electricity.

Embodiments of the present invention may further be used as scrubbers for cleaning various liquids and gases from particulates and smoke.

Embodiments of the invention may also be used as preheaters, superheater of power plants, boiler rooms, condensers, feedwater heaters, Pressure Regulating Valves (PRV), and flow meters.

Embodiments of the present invention may further be used to separate various components and emulsions in various chemical processes.

Embodiments of the invention may also be used in combination with a centrifugal separator to generate electricity and heat energy from geothermal fluid.

Embodiments of the present invention may further be used in the operation of emission control devices.

Embodiments of the invention may also operate as: a vapor compressor for increasing the pressure of the low pressure vapor stream; a two-phase pump for cooling a nuclear reactor; a mixing reactor; means for generating bubbles in the two-phase mixture generating thermal energy; a solar starting pump; an expander for cooling the supply; a condenser for power plant operation; a compressor for power plant operation; a slurry reactor; a slurry reactor; an emulsification mixer; low pollutant emission combustion nozzles; a deaerator; a water recovery device; a coal gasification facility; and in various chemical processes for combining various components and emulsions.

Referring now to fig. 23-32, which illustrate an example embodiment of a direct drive thermodynamic turbine generator in accordance with an embodiment of the present invention, wherein like elements are numbered alike.

Generally, a turbine generator has an inner wheel configured to rotate in a first direction (e.g., clockwise) and an outer wheel configured to rotate in a second direction (e.g., counterclockwise) opposite the first direction. The inner wheel has spoke-like fluid flow channels equipped at their outer ends with one or more KEHs, similar to the KEH20 embodiment described above. The water and steam enter the spoke-like fluid flow channels via flow ports near the inner wheel axis of rotation, combine in the KEH in the manner described above to form single-phase streams, and are discharged from the respective KEH with elevated thrust such that the inner wheel rotates in response to the elevated thrust of the discharged single-phase streams. The outer wheel has a plurality of blades, vanes distributed around the inner surface of the outer wheel in close proximity to the discharge area of one or more KEHs. To further address the elevated thrust of the discharged single-phase flow of one or more KEHs impinging on the plurality of blades, the outer wheel rotates relative to the rotation of the inner wheel. The inner and outer wheels are each connected to a respective shaft, which may be further connected to a generator, compressor, pump or other device capable of producing mechanical and/or electrical energy.

In the embodiment of fig. 23, water 301 and steam 302 enter the turbine drum chamber 325 from opposite sides via side seal bearings 324. The steam and water then enter the two-phase KEH 316 via the independent spoke-like fluid flow channels 318 (similar to the KEH20 embodiment described above). The KEH discharges single-phase fluid that impacts the surrounding blades of the outer wheel 322. The reaction force causes rotation of the outer wheel 322 in the opposite direction of the main turbine (i.e., the inner wheel). The resulting heated discharge water is collected at the bottom of tank 309 and supplied to the customer's heating system via conduit 310. In one embodiment, the shaft 313 is connected to a generator, compressor, pump, or other device capable of producing mechanical and/or electrical energy. The turbine is located in a housing 317. The roller 325 is interconnected with a fluid source through the lateral seal bearing 324.

In the embodiment of fig. 24, water and steam enter the inner wheel through the roller seal bearing 303 and enter the outer housing 304. The housing 304 is equipped with stabilizing brackets and ribs 305. The outer wheel 307 is coupled to the stator 311 by a connection flange 315. In one embodiment, the outer wheel 307 is equipped with modified Pelton (Pelton) blades 308. The resulting heated effluent liquid is collected in tank 309 and supplied to the heating system via conduit 310. The generator 312 is composed of a rotor 314, a stator 311, and a shaft 313. The turbine inner wheel 318 is equipped with a two-phase KEH 316 (similar to the KEH20 embodiment described above). The turbine, which is comprised of an inner wheel and an outer wheel, is located in the housing 317.

In the embodiment of fig. 25, similar to fig. 24, the outer wheel 307 is stationary, while the shaft 312 is configured to drive a generator, compressor, pump or other device capable of generating mechanical and/or electrical energy.

In the embodiment of fig. 26 (similar to the embodiment of fig. 24), the axis of rotation of the turbine wheel is oriented vertically with respect to the horizontal direction, with the axis of rotation of the generator also being oriented vertically.

The embodiment of fig. 27 is similar to that of fig. 25, but with a stationary outer wheel 307 having modified pelton blades 308.

In the embodiment of fig. 28 (which is also similar to the embodiment of fig. 25), the outer wheel 307 is configured to rotate to drive a compressor, pump, or other mechanical device coupled to the connection flange 315, while the inner wheel 318 is configured to rotate to drive another compressor, pump, or other mechanical device coupled to the shaft 313.

In the front view embodiment of fig. 29, it is more clearly shown that the inner wheel 323 is equipped with a plurality of tangential two-phase KEH 321 with respective outlet flow streams arranged to impinge on the blades of the outer wheel 322.

The front view embodiment of fig. 30 is similar to the embodiment of fig. 25, but wherein the bottom of the collection tank 309 is fitted with a tubular heat exchanger 323 for heating the building water.

The embodiment of fig. 31 is similar to that of fig. 25, but the outer wheel is equipped with reflective blades having a different shape.

The embodiment of FIG. 32 is similar to the embodiment of FIG. 23, but has a central supply of steam 302 coupled to the sealed bearings of the turbine. The water supply 301 has a lateral sealing bearing 324 and a direct drive shaft 313.

The embodiments of fig. 33A, 33B and 33C illustrate various design configurations of the turbine.

The embodiment of fig. 34 depicts various heat sources to the turbine, including solar heat 340, a tank 341, a fossil fuel boiler 342, and a steam system, and further depicts the end user: electrical, heating and air conditioning systems.

The embodiment of figure 35 depicts an indirect hot water system supplying steam via a two-phase nozzle, a vortex degasser, a process control pump and a plate and frame heat exchanger.

The embodiments of transonic two-phase reaction turbines described above are operable to gain mechanical energy with minimal thermal kinetic energy loss by increasing efficiency due to the maximum use of multiple waste streams of thermal and kinetic energy of useful working media flowing from the kinetic energy harvester of the turbine.

The embodiments of transonic two-phase reaction turbines described above are operable to address the problem of increased mechanical energy gain in the turbine by increasing efficiency by minimizing energy loss during the throwing away of working medium from the KEH, and also simplify the construction of the turbine.

From the foregoing it will be seen that the scope of the present invention is not limited to one particular embodiment, but encompasses all embodiments falling within the scope of the claims.

While the invention has been described in detail in connection with only a limited number of embodiments, it should be readily understood that the invention is not limited to such disclosed embodiments. Rather, the invention can be modified to incorporate any number of variations, alterations, substitutions or equivalent arrangements not heretofore described, but which are commensurate with the spirit and scope of the invention. Additionally, while various embodiments of the invention have been described, it is to be understood that aspects of the invention may include only some of the described embodiments. Accordingly, the invention is not to be seen as limited by the foregoing description, but is only limited by the scope of the appended claims.

Claims (12)

1. A transonic two-phase reaction turbine, comprising:

at least one rotor comprising a plurality of kinetic energy harvesters;

wherein each kinetic energy collector is arranged and configured to receive a first heat carrier or a plurality of first heat carriers under pressure into a first nozzle and a second heat carrier, which is cooler than the first heat carrier, into a second nozzle, which is arranged downstream of the first nozzle with a distance defined at least partly on the basis of the temperature, pressure and flow of the heat carrier or carriers;

wherein each of the kinetic energy collectors comprises a mixing chamber located between the first nozzle and the second nozzle, the mixing chamber configured to mix the first heat carrier and the second heat carrier to produce a two-phase mixture, the second nozzle placed at the defined distance from the first nozzle for generating an elevated discharge thrust;

wherein each mixing chamber is configured such that the pressure of the first and second heat carriers of the two-phase mixture drops and decelerates to a speed at which at least one or both of the two-phase mixture or the first and second heat carriers boils into a homogeneous two-phase medium with small bubbles, the two-phase medium being a highly compressible medium and having a sonic condition with a mach number greater than 1;

wherein each of the second nozzles is configured to focus and compress a two-phase flow of media, collapsing the small bubbles and turning the two-phase mixture into an incompressible single-phase flow of media with increased kinetic thrust;

wherein each of the kinetic energy collectors further comprises a discharge section disposed downstream of the second nozzle, each of the discharge sections being disposed and configured to discharge the single-phase flow medium with increased kinetic thrust to generate a reaction pressure higher than the input pressure of both the first and second heat carriers to rotationally drive the rotor;

wherein the result is that each of the kinetic energy harvesters produces thermal and kinetic energy.

2. The transonic two-phase reaction turbine of claim 1, wherein:

the at least one rotor includes one or more inner wheels, each equipped with a plurality of the kinetic energy harvesters configured to discharge higher pressure fluid via a focused discharge section.

3. The transonic two-phase reaction turbine of claim 1, wherein:

the at least one rotor comprises feed openings for receiving the first heat carrier and the second heat carrier.

4. The transonic two-phase reaction turbine of claim 3, wherein:

the at least one rotor comprises a hollow duct shaft comprising said supply ports for receiving said first heat carrier and said second heat carrier.

5. The transonic two-phase reaction turbine of claim 3, wherein:

the at least one rotor comprises a combination of a hollow shaft and a solid shaft, and the at least one rotor further comprises a supply port axially offset from the combination of the hollow shaft and the solid shaft for receiving the first heat carrier and the second heat carrier.

6. The transonic two-phase reaction turbine of claim 1, wherein:

each of the discharge sections is disposed in fluid communication with a condenser or a heat exchanger, wherein the single-phase flow medium discharged to the condenser is further usable for heating; and the rotor is disposed in operable communication with a generator, a compressor, a pump, and other mechanical devices that perform mechanical work, wherein reaction torque that rotationally drives the rotor facilitates production of electrical power via the generator.

7. The transonic two-phase reaction turbine of claim 2, wherein:

each of the kinetic energy harvesters is configured to increase the pressure and temperature of a working medium;

wherein the working medium is introduced into the center of the inner wheel through a receiving chamber and an inner channel or into the chamber drum of the inner wheel through a lateral sealing bearing connection;

the tangential section of the inner wheel is provided with one or more of the kinetic energy collectors;

said inner wheel being configured to rotate, thereby increasing centrifugal force of said heat carrier entering said inner wheel, creating higher output pressure and flow rate of said one or more heat carriers, causing pressure elevation of said one or more heat carriers in spokes of said inner wheel, such that said heat carrier flow accelerates into said mixing chamber of said kinetic energy harvester, thereby causing energy exchange between said first and second heat carriers and vigorous boiling of said one or more heat carriers in said mixing chamber of said kinetic energy harvester;

the single-phase flow medium discharged at high pressure and high velocity from the discharge section is accelerated into a direct contact condenser configured to generate reactive thrust in the transonic two-phase reaction turbine and configured to rotate one or more shafts; and

the wheels of the transonic two-phase reaction turbine are configured to operate as pumps to remove exhaust water from the annulus of the casing of the transonic two-phase reaction turbine to complete the cycle of the transonic two-phase reaction turbine, or to supply heat to a heat exchanger, boiler, district heating system, or other user.

8. The transonic two-phase reaction turbine of claim 2, further comprising:

an outer wheel disposed axially about the inner wheel, the outer wheel being equipped with blades disposed to receive the discharged higher pressure fluid from the plurality of kinetic energy collectors, the outer wheel being configured to counter-rotate relative to the inner wheel under the influence of the discharged higher pressure fluid to provide additional mechanical energy;

wherein the resulting reaction forces exerted on the inner wheel and the outer wheel cause the inner wheel and the outer wheel to rotate in opposite directions;

wherein the output generated by rotating the inner wheel and the outer wheel is controllable by an electrical load factor applied to the inner wheel and the outer wheel such that the outer wheel rotates at a lower speed than the inner wheel;

wherein the shaft of the inner wheel is coupled to a generator rotor and the outer wheel is coupled to a stator of the generator;

wherein the axes of rotation of the inner wheel, outer wheel, rotor and stator are arranged in a vertical arrangement or a horizontal arrangement.

9. The transonic two-phase reaction turbine of claim 8, further comprising at least one of: a solar power generation system, heat pump or auxiliary boiler operatively connected to the transonic two-phase reaction turbine for efficient generation of heat, domestic hot water, cooling and electricity.

10. The transonic two-phase reaction turbine of claim 7 operable to cause the working medium pressure in the inner wheel's branches to rise, wherein fluid accelerates, moves into a low pressure zone in the expansion portion of the kinetic energy nozzle and boils intensely, causing supersonic single phase medium to be accelerated at high pressure and speed from the discharge section at a rate of 600ft/sec to 1000ft/sec into a direct contact condenser producing reactive thrust, thereby rotating the one or more shafts.

11. The transonic two-phase reaction turbine of claim 1, wherein:

the at least one rotor comprises at least two wheels configured to rotate in opposite directions, at least one of the at least two wheels being equipped with one or more of the kinetic energy harvesters.

12. The transonic two-phase reaction turbine of claim 11, wherein:

the at least two wheels include an inner wheel and an outer wheel configured to counter-rotate relative to rotation of the inner wheel under the action of high pressure fluid discharged from the one or more kinetic energy collectors.

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