CN108603409B - Conical helical gas turbine with polygonal generator for combined cooling, heating, power, pressure, work and water - Google Patents

Abstract

A conical index spiral for a work extraction or air cooled gas expander. A gas compressor increases air pressure and temperature. The compressor-expander forms a single and simple structure. A generator with a disk pattern using a magnetic circle of varying polarity to induce current in a polygonal solenoid. A small, simple and efficient heat engine, a heat turbine, Firefo Electric. A heat pump, Firefoy Air, is used for cooling, refrigerating, extracting water and heating. Solar power can be generated and stored as compressed air. A water purifier, Jet Aqua, desalinates water by solar energy. Sunlight is concentrated onto the brine column by a sun-tracking conical reflective surface. Solar photovoltaic power may be used to power the screw compressor to condense the low pressure steam. In addition, we re-use solar heat by extracting the heat of the compressed and condensed steam to evaporate more brine under reduced pressure.

Description

Conical helical gas turbine with polygonal generator for combined cooling, heating, power, pressure, work and water

Cross Reference to Related Applications

This application includes the subject matter disclosed in and claiming priority of a provisional application entitled "conical helical gas turbine for combined cooling, heating, power, pressure, work and water" filed on 2/2016 and assigned serial No. 62/290,393, which describes the invention made by the present inventors, with the improvements disclosed in PCT application PCT/US16/40990 filed on 7/5/2016 and PCT application PCT/CN2016/105462 filed on 11/2016. A theme entitled "polygon engine" was submitted on day 27 of 2017, 2 months and assigned serial number 62/460,264.

Background

The world requires clean air, water, food, energy and traffic, which is available and fair to all people, not just developed countries. The key to the widespread supply of these amenities is the technological advancement to meet these needs of people in places supported by local and affordable energy sources (e.g., solar energy and bottled liquefied petroleum gas).

Due to the burning of fossil fuels, which leads to global warming and sea level elevation, we are facing global climate change. Burning coal causes air pollution. The groundwater is rapidly depleted. Global warming is extremely hot and requires more air conditioning using more global warming fossil fuels. Transportation requires expensive petroleum products, causing long-term particulate contamination.

To alleviate energy shortages and climate changes, we emphasize three focus shifts. The first focus shift is from energy generation to energy application. Energy production is only an ultimate comfortable means for clean air, water, food and transportation. Energy savings tend to provide more comfort.

The second focus transfer is from electrical power to heat. We can use heat directly for space and water heating and indirectly to generate electricity for cooling, water, cooking, movement, and then movement induction. Generating electrical power for lighting, communications, computing, and electrical transportation.

We should store energy in a form close to its use: the thermal energy in the hot bath, the pressure energy being the pressurized gas, the cold air being the condensed cryogen or frozen substance, and the electrical energy in the chemical battery. If a small and efficient turbine is available, we should store chemical energy as fuel.

The third focus transfer is the local generation, storage, conversion and use of energy. We wish to reverse the Edison utility model of concentrated production (CG) power using a grid distribution.

We have invented a technique for integrating a disc microturbine with a disc generator. We refer to the Firefly technology, which is personal, but as efficient as large power plants. The CG becomes unnecessary and is replaced by Personal Energy (PE) for mobile collection, storage, conversion and use of energy.

The hit of PE instead of CG in four stages of industrial leather brought us with a complete cycle. The first revolution has focused on the production of large steam engines. The second revolution electrified the world with a large AC generator driven by a steam engine. The third revolution in microelectronics has given us a global computing and communication network. The fourth revolution of MEMS (micro-electro-mechanical systems) reversed the first and second revolution of CG, giving us PE all things to localize, miniaturize, and personalize.

Firefly provides combined cooling, heating, power, pressure, work, and water (acronym CCHP2W 2).

Firefly can help to industrialize poor countries, enabling people to produce where they do not have a power or water grid. Half of the world's people live without a reliable supply of electricity or tap water.

The key to the CCHP2W2 is an efficient microturbine powered by the internal combustion of concentrated solar or gaseous fuel. Integrated with the microturbine is a high efficiency miniature DC motor-generator.

Let us examine the history of heat engines and generators. The first heat turbine was invented by Hero in Alexander harbor 2000 ago. The steam generated in the boiler is sprayed in the opposite direction through the nozzles, thereby rotating the hinged boiler. The Hero turbine is a treasure that is being shown in the alexander library.

Between Hero and the first industrial revolution, wind and water kinetic energy is obtained by turbines (in fact rotating devices, such as wind mills or water mills). The blades or buckets impede the wind or flowing water, causing the turbine to rotate to extract mechanical work.

In 1769 James Watt patented the first powerful and practical steam engine. Steam from a coal fired boiler drives a piston in a cylinder to provide a large force for pumping water, weaving fabric, and driving a train. Steam-powered locomotives bring people to the city. The centralized manufacturing apparatus is driven by a steam engine. These rankine cycle heat engines boil a liquid to produce pressure to perform work.

In 1816, the stockman Stirling patented the Stirling engine. He is concerned with the deadly pressure of the steam boiler. A Stirling engine uses two cylinders, one for heating air and the other for cooling air. The expanding air does work. These Carnot cycle heat engines operate at high temperatures.

In the year 1830, Michael Faraday invented a single pole disk generator. Current is collected from the periphery of the rotating disk sandwiched between the poles of the C-shaped magnet. The damaged eddy current flows within the rotating disk. Despite improvements made, for example, by Nikola Tesla, such generators have not been used for utility generation due to low efficiency and voltage.

In the beginning of the 20 th century, the invention of Edison and Tesla created power enterprises. Steam engines burning coal produce electricity through Tesla's AC generator. Steam engines are large and inefficient. They are strong but slow. To generate large currents, AC generators require large electromagnets.

Nikola Tesla invented a 3-phase generator that mutually induces currents in the stator and rotor coils. The ease of voltage conversion enables efficient high voltage power transmission over long distance grids with greatly reduced ohmic power losses. Power utilities employ AC on DC.

The Nikola Tesla turbine was also invented. The turbine includes a stack of closely spaced disks. The steam is injected tangentially onto the turbine periphery. Steam spirals inwardly between the discs towards the centre of the stack. The steam drags the disc through gas viscosity. Tesla claims to achieve 90% isentropic efficiency of the theoretical Carnot cycle efficiency, which cannot be verified even with today's technology.

Since 1950, gas turbines and steam turbines have made power plants more efficient. Steam turbines powered by steam generated by burning coal have an efficiency of about 40%. A large amount of water is required to condense the low pressure steam from the steam turbine. Combined Cycle Gas Turbines (CCGT) achieve efficiencies above 60%. CCGT uses natural gas to drive a Brayton cycle gas turbine. The hot gas exhaust produces steam to power a rankine cycle steam turbine.

Since the 21 st century, the world has been faced with pollution from burning fossil fuels. The resulting climate change is threatening the survival of humans. However, most of the world's population is still poor due to the water, heat, cold, food and transportation provided. CG degenerates poor countries that lack the power infrastructure. However, the poor population is most affected by global warming, rising sea level and long term air pollution.

Burning more coal is not the answer to help people live a comfortable life. We cannot afford to build an expensive, polluting and wasteful infrastructure of energy collection, generation and distribution. Natural gas and solar energy are the energy sources we have chosen for PE. Both are largely available for personal energy generation and use. PE is efficient, clean, local, small, useful, and therefore aesthetically pleasing.

To address the energy and environmental crisis, we must personalize energy production, storage, conversion, and use. We will concentrate heat as our energy source. The heat may come from solar heat, geothermal heat, or from the combustion of pipeline natural gas and propane transported in tanks.

Our goal is to make small gas turbines as efficient as large gas turbines, with only a fraction of the cost per watt of power. We want cogeneration of heat, cold, water and work in addition to electricity.

We investigated the geometry of the open gas flow in a spiral gas channel that allows the gradual release of gas pressure to obtain work. It is desirable to avoid the sudden conversion of pressure into kinetic energy of the gas by a conical screw. The same spiral gas channel rotating in the opposite direction can also be used as a gas compressor, increasing the pressure and temperature of the gas.

We investigated the geometry for power generation by modern magnetic materials and electronics. Most generators and motors are polar, with multiple poles in the stator interacting with multiple poles in the rotor. We assume that polygonal windings without polarity have a significantly different geometry. Because the polygon rotates in magnetic circles of alternating polarity, the corners of the polygon contain different amounts of magnetic flux. According to Faraday's law of electromagnetic induction, induced electromotive force is related to the change of magnetic flux, and induced electromotive force is generated in the polygonal electromagnetic coil.

Based on our invention of microturbines and microgenerators, we propose three applications. First we describe a thermal turbine integrating a screw compressor, a screw expander and our electrical generator. This heat engine, known as the Firefoy Electric, produces work and electricity.

The microturbine can be used to drive a car to power the drive train directly or indirectly using the electricity it produces. The turbine may be modified as a turbocharger for an automotive piston engine, using tailpipe exhaust to turn a screw expander, which then drives a screw compressor to increase engine pressure. The Firefoy Electric may also be used to fly the drone. It can supply power to the household through solar energy and gas energy.

The second application is the heat pump of an air screw compressor driven by our electric motor to compress air. The heat of compression is used to heat water. The compressed air when cooled discharges water. The compressed air when expanded produces dry and cool air for air conditioning and refrigeration. This technique is known as Firefoy Air.

A third application is a solar powered water desalination system known as a Firefly Aqua. We track the position of the sun and concentrate the sunlight through a conical reflective surface onto a cylindrical tank. Solar energy boils the brine under reduced pressure. Solar energy drives our screw compressor to condense the vapor. Firefoy Aqua has high efficiency because the heat of compression and the heat of condensation are reused to evaporate more brine.

Disclosure of Invention

An outwardly tapering exponential spiral is an effective geometry of the gas flow that converts the internal energy of pressurized hot gases into kinetic energy. We solve the problem of the temperature and pressure drop of the adiabatic gas flow in the outward spiral, pushing the turbine to produce kinetic energy.

The same inward tapering exponential spiral may be an effective geometry for gas compression, converting kinetic energy into pressurized and heated gas when turned in the opposite rotational direction. We have solved the problem of pressure gain of the gas by isothermal compression through a spiral wall pushing the gas towards the center.

We invented a generator based on the relative rotational motion between a circular set of axially magnetized magnets with alternating polarity and a triangular solenoid. The magnetic flux of the magnet passing through the polygonal solenoid varies sinusoidally with the relative motion between the stator and the rotor of the motor. This changing magnetic flux induces an electrical potential between the two ends of the solenoid, thereby converting the rotational power into Alternating Current (AC) power. Three-phase AC power may be generated using three triangular solenoids to form a nine-point star. Direct Current (DC) power may be generated using a gradually shifting solenoid energized by a brush. These generators may also be used as motors that generate motion from electricity.

We have integrated screw compressors and screw expanders with generators and motors for three applications. A first application, known as Firefly Electric, is a thermal turbine that can convert solar or gas combustion heat into work and electricity. Such thermal turbines and motors can drive vehicles such as cars, buses, trucks, trains and small aircraft. It can also be used for powering and heating homes.

A second application, known as Firefly Air, is a heat pump powered by an electric motor to compress humid Air to higher temperatures and pressures. The compressed air is cooled at room temperature to remove heat and moisture, resulting in hot and moisture-condensed drinking water. The cooled and dried compressed air may be expanded in a screw expander to produce work and cold air for air conditioning.

A third application, known as Firefly Aqua, is a solar water desalination system. The focused sunlight from the sun-tracking conical surface heats the brine to boil at less than 100 c under reduced pressure. The low pressure vapor at the head of the heated water column is compressed by a screw compressor using solar energy. Condensing the higher pressure vapor exchanges its heat of compression and heat of condensation to further heat the brine column, producing more low pressure vapor for more potable water. Drinking water is collected at the bottom below the column of evaporated brine.

Drawings

FIG. 1 shows a conical index screw (top), an expander with a clockwise rotating counterclockwise screw (bottom left), and a compressor with a clockwise rotating clockwise screw (bottom right);

FIG. 2 shows the gas temperature drop ratio T/T₀And radius r and Brayton cycle;

FIG. 3 shows the gas compression ratio p₀P cycles with radius r and Hui;

FIG. 4 shows a polygonal generator (FIG. 4a), a polygonal induction motor (FIG. 4b), a rectangular generator (FIG. 4c), and polygonal transducers of frequency and voltage (FIG. 4 d);

figure 5 shows a vertical view of the turbine and generator cross section (centre) and a horizontal cross section view of the expander (top spiral) and compressor (bottom spiral);

FIG. 6 shows a cross-sectional view of a heat pump for heating water and air conditioning;

FIG. 7 shows a cross-sectional view of a solar powered desalination system using a screw compressor;

FIG. 8 shows a conical mirror concentrating sunlight onto a water column at a focal line;

figure 9 shows the scroll compressor in an open position (top image when the spirals are closest together) and a closed position (bottom image when the spirals are furthest apart).

Detailed Description

Conical index helix

The traditional way of compressing or expanding a gas mainly uses two devices: a piston or a fan blade. The gas is enclosed in a cylinder with a movable piston to compress or expand the gas. The gas may also be impinged upon by high speed rotating blades to impart kinetic energy to the gas or to collect kinetic energy from the gas.

We 3D printed the turbine to find the appropriate geometry of the helical airflow channel. We have changed the size and shape of the helix. We have tried Archimedes spirals with radius r ═ a θ + b, which increases linearly with steering angle θ. Tests with pressurized gas have shown that Archimedes helices are less suitable.

We have also tried exponential helices, also known as Bernoulli helices under the name of their inventors. Radius of helix r ═ ae^bθIncreasing exponentially with angle theta. We 3D printed a long narrow exponential spiral with multiple turns. It rotates well but produces little torque. By tapering the shorter length exponential spiral as shown in fig. 1, significant torque is generated.

Exponential helices, such as shells and plants, often occur in nature. The fluid dynamics cause hurricanes to take an exponential spiral shape. The arms of the galaxy are exponential helices. Exponential helices are caused by growth physics. Growth tends to be self-generating and self-similar.

Exponential helices are self-similar: when we enlarge the center of the helix, the helix looks similar. The rotating Bernoulli screw does not visually contract or expand.

This self-similarity is caused by the important properties of the Bernoulli spiral: the helix tangent forms a constant angle with the helix radius. The gas flowing in the Bernoulli screw presses the wall of the screw at a constant angle. In contrast, Archimedes screws extrude the screw wall at a reduced angle.

The hawk surrounds and flies toward the game in a similar manner. Eagle fixated the eye on the game. The eagle is at a fixed angle towards the sight of the game. The distance between the hawk and the prey decreases logarithmically as the hawk turns. This logarithmic spiral is the inverse of the logarithmic spiral.

The exponential spiral has a radius r ═ ae^bθWhere θ is the polar angle in radians. Logarithmic spiral has

For a variable transformation from theta to r,we will use the relationships

The tangent of the helix forming a constant angle with the radius

By r ═ a, the helix length is

Fig. 1 shows a spiral with an outer wall, which is an exponential spiral. The width between the outer wall and the inner wall is shown as a taper. The helical channel width decreases exponentially with the angle theta. We will show that this taper is critical to maintaining gas pressure without accelerating the gas rapidly.

Temperature change of adiabatic expansion of gas in conical helix

The key to our invention is the simple solution of expanding the gas temperature with gas insulation in a conical index spiral. This also demonstrates high thermal to kinetic energy conversion efficiency.

In the early days we used a pressurized air test to drive a narrow, long spiral of constant width. The turbine rotates rapidly but produces little torque. The torque force is important for work production.

Torque is generated by the pressure. To keep the pressure release better controlled, we consider varying the hole area a — wd, the width w multiplied by the depth d of the helix. The gas accelerates due to its internal pressure gradient as indicated by the Navier-Stokes equation. The taper prevents the gas from accelerating due to gas backpressure. We will show that this taper slows the pressure release.

This large torque is caused firstly by the larger area of the outer helical wall than the inner wall and secondly by the greater leverage due to the difference in wall radius from the centre of the helix.

The high pressure and hot gas moving within the spiral has two main energy components. The first component is the internal capacity of the gas due to heat, which is the irregular movement of gas molecules.

The second component is the gas kinetic energy, which is the system velocity of the gas. At the center of the helix where the high pressure gas heats up, the heat energy inside the gas is high. The gas velocity is low.

Most microturbine designs use nozzles to instantly relieve the gas pressure, instantaneously converting the internal energy of the gas into kinetic energy. The gas cools rapidly. After the nozzle, the high velocity gas quickly becomes turbulent. The high velocity gas impacts the turbine blades, producing little torque force. Most of the kinetic energy of the gas is converted back to heat, not work.

We strive not to reduce the gas pressure suddenly. We use the pressure of the hot gas with the hold pressure to generate significant torque forces at the lower angular velocity of the turbine.

Gas kinetic energy density of

Where ρ is the mass density of the gas and v is its velocity. For rho to 1kg/m³And v is 100m/s,

about 5% atmospheric pressure.

According to the ideal gas law, the internal energy density of a gas is pressure

Our turbines operate at pressures in excess of 10. Thus, the gas pressure far exceeds the kinetic energy density.

Bernoulli's law statement

Is constant. For our turbine, pressure is converted to work before the gas accelerates. We will ignore the kinetic energy components in the energy saving consideration.

We consider the torque generated by the pressure acting on the turbine wall. Torque is the pressure p times the spiral wall area

Multiplying the leverage r cos alpha of the torque, wherein

The net torque is the difference between the greater torque force on the outer wall of the channel and the torque force on the inner wall thereof.

The net torque between the outer wall and the inner wall is

For a turbine rotating at an angular velocity ω, the differential torque produces differential power:

the derivation makes the following assumptions. We neglect the kinetic energy of the gas and the viscosity of the gas flow. We assume that the pressure is consumed as work rather than used to accelerate the gas. We also assume that the pressure and velocity of the gas is constant across the radial width of the thin spiral channel.

We now consider the power flow of the gas within the spiral. Taking into account the pressure energy component P of the gas flow_f. The pressure power flow through the area A of the gas flowing at the velocity u is P_f＝Aup。

By conservation of energy, power loss P_fIs the power gain of the turbine. Thus, it is possible to provide

Mass flow conservation means constant Au ρ. Dividing Au rho by the equation to obtain

Relationship of use

The variable transformation from θ to r yields:

from the ideal gas law pV ═ nRT, we have

Molar mass m_wIs the weight of one mole of gas. Thus p/p measures the temperature T of the gas.

By these alternatives we obtain very simple differential equations

The first term is the loss of thermal energy of the gas across the radius. The second term is the work gain of the turbine.

We assume that the airflow is adiabatic, meaning constant TV^γ-1. The gas volume V is proportional to the Au of the gas flow velocity u over the area a. Thus T (Au)^γ-1＝T₀(A₀u₀)^γ-1To obtain

We use a constant w and varying depth

The depth is chosen to taper linearly with the radius r of the channel. For r ═ r₀Note that d ═ d₀. Since the radius and length of the spiral channel increase exponentially with angle θ, the channel depth d increases with channel length

Decreases exponentially.

Using this channel geometry, we obtain a differential equation

When r is r₀When the initial condition is T ═ T₀. The solution of the differential equation is

FIG. 2 is the temperature T/T through the turbine₀Ratio of decrease to use

Radius r of 0.2, 0.4, 0.6, 0.8 and 1.0₀＝1cm≤r≤r ₁4 cm. We select r₀＝1cm，d₀2cm, maximum helix radius r₁4cm, c 0.2, w 0.3cm, and γ 1.4.

Efficiency is

Wherein the high temperature T after combustion_H＝T₀And low gas exit temperature T_L. In that

And the efficiency is as high as 60 percent. At ω 377rad/s (60Hz), u₀377cm/s, wind speed (less than 15 km per hour). The gas was cooled from 1000K to 400K (127 ℃).

Pressure change of gas compression in exponential spiral

The exponential spiral expander compresses gas rather than expands gas when rotating in reverse. For adiabatic gas expansion, p^1-γT^γIs constant. Using this constant value, the pressure p over the helix radius r can be derived from the temperature drop equation.

Pressure increase p₀Obtained from the following equation:

centripetal gas pressure p₀Is directed towards the center and has a velocity u₀As a result of the gas flow of (a).

If the gas is directed outwards with a negative u₀And conversely, the pressure p increases towards the disc periphery. That gas compression towards the outside is a centrifugal compressor used in the first generation jet engines invented during world war ii. Unfortunately, centrifugal compressors provide only a slight pressure increase in the radial and centrifugal airflows. Subsequent development of jet engines has sought to increase the pressure of the air stream axially rather than radially through the use of multiple stages of turbine blades that increase air pressure in one stage.

It is believed that centripetal compression is better than centrifugal compression for high compression ratios, which can lead to better turbine efficiency. For centripetal gas compression instead of centrifugal gas compression, the compressor rotates in the opposite direction, pushing the gas towards the center. The gas spiral must taper towards the periphery of the turbine to draw gas in the spiral and push it towards the centre. The air flow slows down towards the center, converting its kinetic energy into pressure energy. Flow velocity u at the center of the conical reduction₀Increasing the ratio

Ratio in the above equation for increasing compression ratio

Is very important.

We describe herein a multistage radial compressor. The conical index screw expander (lower left, counterclockwise screw rotation in fig. 1) is placed on top of the conical index screw compressor (lower right, clockwise screw rotation in fig. 1). We can use the space within the spiral of both the expander and the compressor to further compress the gas.

We design the airflow direction as follows. The gas flows from the outside to the inside between the conical spirals in the screw compressor. Midway, the gas flows into the space between the conical spirals within the spiral expander. The gas flows from inside to outside in the space, and the gas is accelerated under the action of centrifugal force. At the periphery of the screw expander, the gas flows into the tapered end of the screw compressor passage. The gas is triple compressed and appears in the center of the compressor. The order of compression is: first conical centripetal compression, followed by centrifugal compression and finally centripetal compression.

The multi-stage compression of the interstage cooling reduces other temperatures. We consider that isothermal gas compression requires heat exchange between the gas and the outside world. Isothermal gas compression requires less energy than adiabatic gas compression. The heat loss from the compressed gas helps cool the gas as it expands.

For isothermal processes, work dW performed by the compressed gas_TGenerates heat dQ, wherein

This heat is transferred to the environment. Conservation of energy means

For an isothermal process, pV ═ nRT is constant for constant T. The speed u satisfies the following condition: for a given value A₀、u₀、p₀，Aup＝A₀u₀p₀Is a constant. The above differential equation becomes:

with a similar coning factor c, solving the above differential equation, we get the pressure ratio:

this pressure increase is much less than the pressure increase of the inwardly tapering spiral. FIG. 3 plots pressure ratio for isothermal compression versus ratio

r is at r₀＝2cm≤r≤r₁In the range of 16 cm. The taper factor is c 0.025 and the width w 1 cm. Unknown discharge velocity u₀By pressure at both ends of the helix (i.e. p)₀And p₁) And (4) determining. For a given

Velocity u₀Will adjust to the solution of the above equation.

The pressure increases linearly with the angular velocity ω and the compressor radius. Compression with flow velocity u₀Slowing down and increasing. More work needs to be done to compress the slow flowing gas. Flow equation A by isothermal compression₀u₀p₀Conservation of Aup, the flow velocity u₀With edge flow velocity u₁And (6) associating. Will be provided with

Substituting the pressure ratio equation:

for c 0, isothermal compression reduces the speed to

Novel generator and motor

We wish to invent generators and motors having the same overall dimensions of the disks as our helical turbine. Pioneers like Edison, Tesla and Steinmetz were frustrated by the technologies available at the time. The first problem is the lack of powerful permanent magnets. Due to the lack of powerful permanent magnets, large electromagnets have to be used to induce power. A second problem is the lack of high speed heat engines, such as modern gas turbines. The magnets must be powerful to convert the slow but large torque of the steam engine. A third problem is the lack of solid state electronics for digital and solid state control of voltage and current.

Modern technology addresses these problems. Rare earth magnets produce strong magnetic fields. High speed turbines run much faster than piston steam engines. Solid state high power electronics provide flexible control of voltage and current. Digital electronics can synthesize AC of variable frequency, phase and amplitude. Our generator is simpler and more compact than the Faraday or Tesla generator.

Figure 4a shows how power is induced in 3 triangular solenoids by the relative motion of a ring of 6 magnets with alternating polarity. The magnet ring induces electrical power in the polygonal solenoid. The magnetic flux through the solenoid varies in a sinusoidal wave, inducing an electrical potential between the two ends of the solenoid according to Faraday's law of induction, converting the motion into an alternating current.

The polygon for the solenoid may be a triangle, square, rectangle, or pointed star, etc. The polygon includes magnetic flux that changes as the magnet ring having alternating magnetic poles is coaxially rotated.

The stator coils comprise a plurality of triangular turns of magnetic wire or tape. As the magnet ring rotates, the triangular coil does not overlap with the magnet (north or south polarity).

The magnet in fig. 4a has a radius r. The center of the magnet is located 6 away from the center of the circle. Three triangles are wound on an outer circle with a radius of 8. As shown, the upright triangle is defined by all 6 magnets. There is no net magnetic flux within the triangle.

When the rotor is rotated 30 ° clockwise, the triangle contains exactly the same polarity (north in the figure) of the magnet flux. When the rotor rotates another 30 deg., the net magnetic flux is again zero. When the rotor is turned another 30 deg., the triangle contains completely the magnet flux of the opposite polarity (south in the figure). At a total of 4 x 30 ° -120 ° of complete rotation, the triangle again contains zero net flux. The flux varies sinusoidally with three cycles per 360 ° of rotation.

The electromotive force (EMF) between the terminals of the N-turn triangular solenoid is, according to Faraday's law of induction, as

The rate of change of the magnetic flux Φ with time t. The flux Φ in each triangle of 3 magnets with magnetic field strength B has a peak Φ at the apex of their area _max3 BA. The induced EMF at the rotation frequency f is v (t) ═ 3NBA × 2 pi × 3f × cos (2 pi × 3ft) ═ 18 pi f NBA cos 6 pi ft.

If we use three triangles rotated 40 deg. relative to each other, a three-phase AC with a common neutral is produced. The three triangles form a nine point star as shown.

The AC generator may be used as a motor. The force vector dF is the vector product of the current vector i with the length vector dl and the magnetic field B, by ampere force law dF ═ i × dl × B. EMF power dissipation p (t) v (t) i (t). The EMF is converted to mechanical force.

The rotational speed of the rotor depends on the force balance between the EMF and the mechanical load. In the absence of mechanical load, the final speed of the rotor is determined by the voltage amplitude v (t). The voltage v (t) and current i (t) are 90 ° out of phase, with no net electrical power dissipated over time.

When we increase the mechanical load, the rotor speed decreases. The induced EMF decreases. However, the phase difference between the current and voltage changes, resulting in dissipation of the EMF to produce motion.

Thus, the speed of the motor is determined by the voltage and the torque force is determined by the current. For AC motors, an Electronic Speed Controller (ESC) is required to control frequency, voltage and current. The ESC controls the frequency and hence the rotational speed by digital pulse width modulation.

Since the motion between the triangle and the circle is relative, the triangle role as the stator and the circle role as the rotor can be interchanged. We can fix the magnet ring as a stator and rotate the triangle as a rotor.

The motor of fig. 4a can be modified as an induction motor, as shown in fig. 4 b. Instead of a magnet rotor with alternating polarity, a circular conductor disc can be used to generate a magnetic field of varying polarity. As a motor, polyphase AC generates a rotating pattern of varying polarity magnetic fields. This rotating magnetic field induces a reactive current through Lenz's law, thereby opposing the magnetic field generated by the induced current in the polygonal winding.

To operate this polyphase AC induction machine as an AC induction motor, the motor first needs to be prepared for movement. The initial motion induces a magnetic field in the circular conductor disc.

FIG. 4c shows another embodiment of a polygonal AC motor. The rotor comprises 4 magnets of varying polarity. Each magnet has a radius r. The center of the opposite magnet of the same polarity is 4r from the center. Each solenoid is rectangular with dimensions of 2 x 6 r.

As the rotor rotates, each rectangle may include two north poles of magnetic flux, no net flux, or two south poles of flux. Instead of the 3 AC cycles of the generator in fig. 4a, two AC cycles are generated per complete rotation. For use as an AC motor, the motor speed is high. When driven by 60Hertz alternating current the motor of fig. 4a rotates at 1200rpm, whereas the motor of fig. 4c rotates at a higher rotation speed of 1800 rpm.

The transducers for AC frequency and voltage are shown in fig. 4 d. The transducers comprise a different number and polygon type of motor-generator series connection for the motor and generator. As shown, the motor uses two rectangular windings, as shown in fig. 4c, while the generator uses six triangular windings, as shown in fig. 4 a. The AC frequency from the generator is 3 times higher than the AC frequency of the drive motor. The AC voltage depends on the rotation ratio of the generator and the motor.

The motor or generator in fig. 4d does not require a rotor. The two rectangular windings generate a magnetic field to induce a voltage in the six triangular windings. This frequency and voltage transducer is similar to a voltage transformer without moving parts.

First application of conical helical turbines: gas turbine with generator

Our thermal turbine uses a Brayton thermodynamic cycle to convert heat into work. The pressure versus volume plot of the Brayton cycle is shown at the bottom of fig. 2. The Brayton cycle comprises four phases: adiabatic and isentropic compression of air 1 → 2, isobaric heat addition and expansion of gas 2 → 3, adiabatic and isentropic expansion of gas 3 → 4, and isobaric cooling of gas after the turbine 4 → 1.

The Brayton cycle heat engine efficiency was analyzed as follows. Consider the temperature T and pressure p of the gas in the Brayton cycle. Adiabatic compression of gas (1 → 2) constant pV^γAnd TV^γ-1. For a diatomic gas, the adiabatic coefficient is 1.4. Let us assume that the air and fuel are at a pressure of 1 bar and a temperature of 300K (27 c). The adiabatic compression volume was multiplied by 8 times to increase the pressure to 18.38 bar and the temperature to 689.2K (343.3 ℃).

When the fuel-air mixture is combusted at a constant pressure (2 → 3), the heat of combustion causes the volume of the combusted mixture to increase, producing work as the volume expands. After isobaric expansion, the combusted air expands further as the pressure drops toward the spiral outlet (3 → 4). Further work is generated by adiabatic expansion of the gas within the spiral. The exhaust gas is cooled externally (4 → 1).

Work W is given by the area in the pressure versus volume graph of the Brayton cycle. For adiabatic expansion, pV^γIs constant. Pressure P_LAnd P_HLow pressure before the compressor and high pressure after it. Volume V_LAnd V_HIs the low pressure volume before the compressor and the high pressure volume after it. The work done by the Brayton cycle is

The constant C, C' depends on the initial conditions of the gas volume. For each cycle, renormalized by the heat of combustion Q, the efficiency of the Brayton cycle heat engine is

The Brayton cycle has a constant pressure (isobaric) in two steps of the cycle, pressure P_LAnd P_H. Efficiency depends on pressure ratio

Or compression ratio

Carnot heat engine efficiency of

Given that it depends on low and high temperatures

If we assume a volume compression of 8 by the compressor, then according to the constant pV^γThe pressure increased 18.38 times.

The Brayton cycle efficiency is

An embodiment of a Hui heat engine is shown in FIG. 5. At the bottom of the heat engine is the compressor cylinder. An alternative compressor that may be used is the Archimedes scroll compressor shown in fig. 9. The top is the expander cone, which has a constant width spiral with a tapered depth. The compressed air flows from the top center of the compressor to the bottom center of the expander. Fuel flows from the bottom center of the compressor through the small tubes and ignites in the central combustion chamber of the expander. The pressure of the expanding combusted air causes the individual compressor-expander assemblies to rotate, providing motive power. The electricity is generated by a homopolar generator at the bottom of the assembly.

Second application of conical helical turbines: motor-driven heat pump/dehumidifier

Heat pumps and chillers typically use refrigerants such as Hydrofluorocarbons (HFCs). Compressing the HFC gas pumps heat into the pressurized HFC, which liquefies upon cooling. Evaporating the liquid HFC under reduced pressure removes the heat from the environment. The liquefaction-evaporation cycle constitutes a rankine cycle thermodynamic pump process. However, if the refrigerant (e.g., HFC) is released into the atmosphere, it is an effective global warming gas. HFC captures 1000 times more heat than carbon dioxide. Rapid HFC replacement is scheduled according to the latest Kigali protocol.

The aircraft uses an alternative air conditioning method that instead uses the Brayton cycle thermodynamic pump process. Air is discharged from a compressor of the jet engine. A slight decrease in air pressure rapidly cools the exhaust air. The cool air from the cabin vents is typically misty. The mist further cools the air as the mist evaporates. The humid air upon compression is hazy and fogged. If we cool the compressed humid air, we can remove the moisture from the air and produce water for consumption. Condensing the moisture in the air also drives off the heat of vaporization of the water in the air. Thus achieving more heat removal.

This observation motivates the use of a Hui screw compressor to produce cold air and water condensate. We explain here the thermodynamic advantages. We introduce here a new thermodynamic heat pump process, which we name the Hui cycle as shown at the bottom of fig. 3. The Hui cycle combines two thermodynamic cycles: carnot cycle with isothermal and adiabatic stages and Brayton cycle with isobaric and adiabatic stages. We replaced the adiabatic process of the Brayton cycle with an isothermal process. Isothermal compression reduces the amount of work required. Isothermal expansion increases the work produced using ambient heat from the environment.

The Hui cycle requires a compressor and an expander with built-in heat exchangers. Heat exchange may be achieved by ambient air flow between the spiral channels. The Hui cycle being shown in FIG. 3And (4) each stage. There are three temperatures: ambient temperature T_aHigh temperature T for extracting heat_HAnd a low temperature T for generating cold air_L。

Stage 1 → 2 is gas at T_HIsothermal compression stage of time, compression work W is required_c＝nRT_H lnp_H/p_LWherein p is_H、p_LIs the high and low pressure of the isobaric stage. Without increasing the temperature of the gas, the work is completely changed into the dissipated heat of compression Q_c。

Stage 2 → 2a is gas from high T_HTo environment T_aIsobaric cooling. Stage 2 → 3 is gas from the environment T_aTo low T_LFurther isobaric cooling.

Stage 3 → 4 is gas at low T_LIsothermal expansion phase of time, by heat of absorption Q_eGenerating expansion work W_eWherein Q is_e＝W_e＝nRT_L lnp_H/p_L。

Stage 4 → 4b is gas from low T_LTo environment T_aIsobaric heating. Stage 4b → 1 is the gas from the environment T_aTo a high T_HFurther isobaric heating.

We reuse the heat using a counter-flow heat exchanger. For stage 2 → 2a, the heat given off is just absorbed by stage 4b → 1. For stage 2a → 3, the emitted heat is just absorbed by stage 4 → 4 b.

We summarize the heating and freezing performance as follows. Coefficient of heating Performance COP_hIs the amount of heat Q generated_hDivided by the net work done W_net＝W_c-W_e. Thus, it is possible to provide

Coefficient of cooling performance COP_cIs cold gas Q generated by isothermal expansion_eDivided by the net work done W_net＝W_c-W_e。

Thus, it is possible to provide

Considering water from T_aHeating to T at 27 deg.C (300K)_H77 ℃ (350K) and air from T_aCool to 7 ℃ (280K) at 27 ℃ (300K). We obtain

And

conventional refrigerant refrigerants for refrigeration compression, such as ozone depleting CFCs or heat retaining HFCs. We should compress air directly rather than compressing refrigerant. The Hui cycle can achieve a desired thermodynamic pump efficiency. Work is recovered from the expanding gas. In contrast, evaporating the refrigerant produces no work. In the case of efficient air compression without a high compression ratio, liquefaction of the refrigerant is preferable. Much research has been directed to finding effective refrigerants that do not harm the environment. With a compact helical turbine we can compress air efficiently. Therefore, we can avoid the use of refrigerant.

More preferably, the compressed humid air condenses moisture in the air while removing the heat of compression. The heat of condensation is dissipated. Conventional air conditioning requires the use of cold air generated by the evaporation of refrigerant gas to remove moisture and its heat of condensation. For the same air temperature drop, dehumidifying the air increases the workload of the air conditioner.

The condenser of the conventional air conditioner is located outside a building, and condenses moisture that is generally dropped on a human body. For our proposed air conditioner, we contain the condensed moisture within a closed condenser. The collected moisture may be drained through a pipe or collected for human and plant consumption.

Evaporating water exerts a vapor pressure which depends only on the temperature. The steam pressure is a fraction of the pressure exerted by the humid air. Each component gas of air exerts its own vapor pressure. The air composition comprised oxygen (19 vol%), nitrogen (80%), argon (1%) and water (percentage based on moisture level). Atmospheric pressure is the sum of the vapor pressures of the various air components. The total steam pressure is about 1 bar at sea level.

The humidity of air is defined as the water content in the air divided by the water content in 100% humid air. The dew point is defined as the temperature when the air is cooled to the point where water begins to condense in 100% humid air. The dew point and air temperature are the same, with 100% humidity. For example, 100% moist air at 25 ℃ and 14 ℃ contains 2 g water and 1 g water, respectively, for 100 g air. Thus, the dew point of 50% humid air at 25 ℃ is 14 ℃.

What will air moisture happen if we double the pressure of 100% humid air at 25? Initially, the vapor pressure of all air components doubles. The moist air heated by compression is cooled back to 25 ℃. Since the water vapor pressure depends only on the temperature, the increased water vapor pressure due to the compression causes water to condense. Half of the air water vapor will have to condense out to recover the same vapor pressure as water at 25 c.

For high humidity air, if we compress the air volume 2 to 4 times, most of the moisture in the air will condense out. This condensation releases a large amount of condensation heat. Consider a 2-fold increase in pressure of 80% humid air at 25 ℃. The air had 1.6 grams of water per 100 grams of humid air. Increasing the pressure and subsequently cooling the humid air will force 0.6 grams of water to be produced. At a heat of evaporation of over 2200 joules per gram of water evaporated, the pressure would remove 1321.2 joules of energy for 0.6 grams of water condensed.

This heat is significant compared to the cooling of air. Consider the latent heat of cooling 100 grams of air to 20 ℃. The heat to be removed by freezing is

Four times the pressure of 80% humid air at 25 c will force the generation of 1.2 grams of water vapor with a heat of condensation of

More heat is removed than by cooling the air to 20 c. The water removed from the air is used as water for human or plant consumption.

Fig. 6 shows a heat pump for generating hot water, cold air and condensed water. The top compressor, driven by our electric motor, compresses air into the heat exchange tubes from the bottom center of the compressor. The tube passes through the center of the tank and receives its heat of air compression and water condensation to heat the water in the tank. The condensed water and the cooled compressed air are collected at the bottom tank. The compressed air drives the expander at the top, resulting in cool air for space cooling. Compressed air can also be distributed through nylon tubing to the indoor expander for refrigeration and for work production and for electricity for lighting and appliance consumption.

A third application of the conical helical turbine: solar energy water desalination

We can use a screw compressor for solar desalination of water. The electrical power used to drive the compressor may be generated from solar thermal power or photovoltaic power. Solar energy can be concentrated and collected as heat to boil seawater under reduced air pressure. Our screw compressor can be used to condense the vapor from solar evaporated brine. More brine can be evaporated using the heat of condensation. Thus, efficient water desalination can be achieved.

Solar desalination is inspired when i hear a loud hissing sound in tibet in china and see steam coming out of the solar water heater. The low pressure in tibet causes the water to boil at temperatures below 100 c. When the atmospheric pressure is halved, the water boils at 80 ℃.

We can re-establish this low pressure environment at the head of the high water column. The water boils at 80 ℃ at the top of the 5 meter water column where the pressure is halved. The 10 meter water column has zero pressure at the top where the water will evaporate a lot. The resulting vapor pressure causes the water column to drop. We will need a pump to remove the vapor in order to create a near vacuum at the top.

Fig. 7 shows a novel solar water desalination plant. For a conventional solar water heater, solar heat is captured to heat water in a glass tube. The glass tube is contained in another vacuum glass tube. The outer glass tube has a reflective half surface that reflects sunlight onto the inner water heating tube. Like solar water heaters, we use larger light reflectors. The reflector is shaped like a conical surface as shown in fig. 8 to concentrate sunlight onto a vertically placed water pipe. The reflector tracks the sun in azimuth position alpha. The sun has α ═ 0 due to north and south. The reflector also tracks the sun in height or elevation, defined as the angle β of the sunlight to the horizon. The sun directly above the zenith has a β of 90 °. The sun on the horizon has β ═ 0 °.

Fig. 8 shows a conical reflector, which is a part of the curved surface of a cone. We refer to the center line of the conical surface as the apex line. The apex line should follow the azimuth position of the sun. To track the sun in its height, the apex line is tilted at an angle δ from the zenith so that the reflected light shines horizontally on the vertical brine column.

The horizontal cross section of the conical surface is parabolic focused on the vertical z-axis. Consider the sun on the zenith directly above the zenith having β -90 °. If the apex line is tilted δ 45 °, overhead sunlight is reflected horizontally onto the brine column. The reflector is conical, i.e. the cone is formed by rays from the origin (0, 0, 0).

Consider the elevation of a conical surface as shown in fig. 8 at δ equal to 45 °. The tip of the cone is located at the origin (x, y, z) ═ 0, 0, 0. The brine column is centered on the z-axis. The parabolic cross section at level z has an apical minimum at (x, y, z) ═ 0, z, z. If the sun is directly above the vertex β 90 °, the light is focused to (x, y, z) ═ 0, 0, z with a focal length p ═ z. For a given vertical level z, the parabola at the level z is x²4p (z) (y-p (z)), where p (z) is the focal length of the parabola at the level z.

Consider the more general case beta>0. We wish to reflect sunlight so that it strikes the vertical column horizontally. The resulting inclination of the tip line is

For the sun on the zenith β -90 °, the tilt is δ. The top line is the equation y-z tan δ on the y-z plane. The conical surface is represented by equation x as shown in FIG. 8²Given as 4z tan δ (y-z tan δ). The conical surface is curved, i.e. a flat piece of reflective material can be placed on the surface of the cone. The focal length at level z is z tan δ.

While it is important that the reflector tracks the sun well in azimuth position, it is less important to be able to accurately track the sun in elevation. The resulting focal line remains on the z-axis, but the line can move up or down on this axis depending on the height of the sun. It may therefore be sufficient for the reflector to be preset with an inclination of δ, for example, 30 °, 60 ° and 90 ° for the height β of the sun, respectively, 15 °, 30 ° and 45 °.

The reduced pressure at the head of the water causes the water to boil at a lower temperature. When the vapor pressure of the water is equal to ambient pressure, the water boils. The steam pressure depends only on the temperature. As shown in fig. 7, a key step for water desalination is to compress low pressure water vapor to condense at a higher pressure. A screw compressor is placed above the head of the water to remove the steam.

The compressed and heated water vapor emerges from the center of the screw compressor into a long thin tube down the center of the water column. The water condenses into steam, generating heat that is exchanged with the surrounding boiling water. As shown in fig. 7, the condensed water is collected in a closed container at the bottom of the column. Fresh water may be pumped out of the condensing chamber.

As the water vapor condenses, it generates a large amount of heat of condensation. Capturing this heat of condensation significantly increases the efficiency of water distillation.

In the waterhead part, the salinity is evaporated and concentrated. This heavy and hot brine solution is discharged after its heat has been introduced into the incoming brine through a counter-flow heat exchanger.

The efficiency of desalination has thermodynamic limitations. Evaporating the salt-containing water requires more heat than is released by condensing the steam. In addition, the compression of steam by a helical turbine requires work that is converted into heat of compression. However, these additional energies required can be supplied in large quantities by solar thermal power and solar photovoltaic power. Heat is lost by convection outside the brine column. With good insulation and heat exchange we expect high efficiency.

The power for operating the compressor may be supplied by a solar photovoltaic cell. The electricity is used to compress low pressure water vapor. The kinetic energy is converted into heat of compression. Both the heat of compression and the heat of condensation are used to evaporate the brine more.

The main mode of thermal desalination employs multi-stage flash evaporation. The seawater is heated by fossil fired power plants. The hot seawater is flashed into successive stages of evaporation chambers using progressively lower pressures. We use a screw compressor instead of staging.

Drinking saline water has become a health problem in the indian subcontinent. Pacific island citizens can also utilize solar energy for desalination for drinking and cleaning purposes. We expect that new solar desalination methods will be of significant help to coastal people without the use of polluting and expensive fossil fuels.

Detailed description of conical index screw expander and compressor

Figure 1 shows a conical index screw (top) and its embodiments as an expander (bottom left) and compressor (bottom right).

The spiral has an outer wall 001, the outer wall 001 including a radius 002 having a turning angle θ. The length of the radius is indicated by 003.

The spiral has an inner wall 004 of smaller length than the outer wall. The radial distance between the inner wall and the outer wall decreases exponentially with the steering angle having a width indicated by 005.

The starting end of the spiral channel 006 is wider than the end of the spiral channel 007. The air flow depends on the direction of rotation of the spiral. If the spiral is rotated in a clockwise direction, the gas flows from the inside to the outside by centrifugal force. The gas flowing out expands. If the spiral is rotated in a counterclockwise direction, gas flows from the outside to the inside by a centripetal force, thereby compressing the gas flowing in.

An embodiment of a conical exponential spiral expander 101 is shown in the lower left hand disc of figure 1, comprising a plurality of 4- spiral channels 102, 103, 104, 105, each spiral channel spiraling outward in a counter-clockwise direction. This plurality allows more gas to flow in the disk, thus enhancing the power of the turbine. The spiral turbine disk 101 rotates in a clockwise direction as indicated at 110 in response to gas flowing counterclockwise in these spiral channels.

For spiral channel 102, gas flows 1.5 revolutions from spiral inlet 108 before reaching spiral outlet 107. The gas flowing counterclockwise presses the outer spiral wall of the spiral channel 102. For spiral channel 105, the direction of airflow is indicated by the arrows from inlet 108 and at outlet 109. These two arrows indicate a 1.5 turn counter clockwise flow.

For the spiral channel 102, the outer wall of the spiral compresses the two portions. For the

The first portion 106 has a faster exponentially growing radius. For this range of θ, there is no inner wall: gas enters the helix 102 through the gas entry central bore 108. For the range

The inner wall of spiral 102 is the outer wall of spiral 103. For the range

The inner wall 107 of the spiral 102 is the outer wall of the spiral 102 minus the constant spiral width w for this range theta.

As the radius r expands exponentially in theta, the helical bore may taper through the depth d of the helix, which decreases exponentially in theta relative to d, which decreases linearly with the radius r. Thus, when viewed from the side, the disk expander resembles the cone 513 as shown in fig. 5.

When rotating in the opposite, counter-clockwise direction, the same expander 101 can become a gas compressor compressing gas from the outside inwards towards the centre of the spiral disc.

The lower right of fig. 1 shows a compressor 111 with 4 exponential spirals 112, 113, 114, 115 from the inside outwards in a clockwise direction. Such a plurality allows more gas to flow in the disk. The helical turbine disk 111 rotates in a counter-clockwise direction as indicated at 120. The motive force for such counterclockwise rotation may be provided by a helical expander 101 rotating in the same clockwise direction. The screw expanders may be stacked on top of the screw compressor as a single gas turbine as shown in fig. 5, with the coaxial expander-compressors rotating in the same clockwise direction.

The screw compressor 111 may be driven by a motor. For the compressed condensation of low pressure steam from the evaporated salt-containing water in fig. 7, the motor drives the compressor.

For the spiral channel 112, the gas flows 1.5 turns from the outer spiral inlet 112 before reaching the spiral outlet 118 at the center of the spiral disk 111. The gas flowing counterclockwise is pressed by the outer spiral wall of the spiral passage 112, and the pressure of the gas increases as it flows toward the center of the spiral disk. For spiral channel 115, the direction of airflow is indicated by the arrows from inlet 119 and at outlet 118. These two arrows indicate a 1.5 turn counter clockwise flow.

The depth of the helical channel may taper from the centre to the outside. The gas flow from the outside to the inside is decelerated due to the expansion of the spiral depth from the outside to the center. Regardless of whether the spiral is tapered or not, the gas decelerates as it compresses to a smaller volume.

Gas may be allowed to flow between the spirals driven by the rotational motion of the turbine disc. The gas flowing between the spirals may exchange heat with the gas flow inside the spirals. For gas compression, the compressed gas inside the spirals may be cooled by the gas flowing between the spirals, achieving a more isothermal than adiabatic compression. For gas expansion, the expanding gas inside the spirals can be heated by the gas flowing between the spirals, providing more motive force for gas expansion.

These screw compressors and expanders may be operated in stages. The compressor 111 may be stacked coaxially with the expander 101, with gas flowing through a shared center of gas to flow from the center 118 of the compressor 111 to the center 108 of the expander 101. The compressors may also be stacked coaxially for higher compression ratios, with gas passages flowing through radial conduits from the center 118 to the inlet 112. The expander may also be stacked coaxially with a similar radial passage from the outlet to the inlet.

Detailed description of the generator

Fig. 4 shows an embodiment of a three-phase AC generator 401 with three triangular stator induction coils 402, 403, 404 for the output phases 405, 406, 407 and a circular magnetic rotor 408 with alternating polarity permanent magnets 409, 410, 411, 412, 413, 414 with marked north (N) and south (S) poles. Since the movements are opposite, the induction coil can also rotate in the static magnet ring.

The magnets are equally spaced around a radius circle centered at 415, which 415 is also the axis of rotation. The magnets are axially magnetized. Each magnet is placed in a socket in the rotor. The bottom of these magnets are placed on a plate 416 with high magnetic susceptibility to flow magnetic flux between alternating poles on the plate. This allows easy penetration of the magnetic field.

The other end of these magnets is an air gap, such as the air gap labeled 417. Above the air gap is another plate 418 having a high magnetic susceptibility. The plate allows the magnetic field to easily penetrate between the poles penetrated by the magnets across the air gap. The plates 416, 418 may be connected by a hollow cylinder 419 to allow magnetic flux to flow between the plates.

Triangular stator coil 402 has three sides 420, 421, 422 and three included angles 423, 424, 425. The side 420 is located just above the pair of magnets 412, 413. Similarly, side 421 is located just inside magnet pair 410, 411, and side 422 is located just inside magnet pair 409, 414. Triangular stator coils 403, 404 are similarly defined by a pair of magnets.

The three coils form a nine-point star with all corners of the solenoid fixed to the stator housing 426. The 3 triangular coils are shifted 120 deg., 360 deg. one turn 1/3 relative to each other. The coil 402 has a net zero magnetic flux. Coil 403 includes a south-facing magnetic flux of about 2/3. Coil 404 includes a north-facing magnetic flux of about 2/3.

As the magnet coils rotate, the magnetic flux within each coil changes. It can be seen more easily how the flux in the coil 402 is changed in each step of 30 counter-clockwise rotation by rotating the coil 402. The corner 425 moves to 427 containing all the magnetic flux from the north pole of the magnet 409. The corner 423 moves to 428 containing all the magnetic flux from the north pole of the magnet 413. The corner 424 moves to 429 containing all of the magnetic flux from the north pole of the magnet 411. The coil 402 has a maximum north-facing magnetic flux.

If the triangular coil 402 is rotated another 30 counterclockwise relative to the magnet coil, the corners 430, 431, 432 contain no poles, so that the net magnetic flux is again zero.

If the coil 402 is rotated another 30 counterclockwise, the corners 433, 434, 435 contain the south poles 414, 412, 410, respectively. The coil 402 has a maximum south-facing magnetic flux.

If the coil 402 is rotated further counterclockwise by 30 deg., the corners are now at 423, 424, 425 returning to the initial position of the coil with zero net magnetic flux within the triangle.

The coil makes four 30 ° turns for a total of 120 °. EMF output 405 completes a 360 ° phase change. If the rotor is rotating at a frequency of fHz, each phase has a frequency of 3 Hz.

The two other coils work similarly. Since the three coils are offset from each other by 120 °, the power outputs are also offset from each other by 120 °. The three output loads 436, 437, 438 consume the generated electrical power. As the load increases, the rotational speed slows down, the voltage drops, and the current increases.

The same power generation device may operate like a motor to convert power into motion. The output loads 436, 437, 438 are now the outputs of the electronic speed controller ESC. The controlled frequency, voltage and current generate a torque on the rotor to drive the mechanical load.

The polygonal motor may be modified to the polygonal induction motor shown in fig. 4 b. The polygonal induction motor is a rotor centered on a shaft 439. The rotor uses a circular conductor disk 440 instead of a rotor of variable polarity magnets. Lenz's law states that magnetic action and reaction are equal and opposite. The polygonal windings induce current in the circular conductor disk 440. The opposing magnetic fields in the stator and rotor produce motion.

In fig. 4b, the single phase AC power source 441 induces a varying magnetic field in the coil 442 mounted on the stator 443. The coil 442 induces a current in the disk 440. A rotating magnetic field of varying polarity is generated. To initiate rotation in the desired direction, capacitor 444 is used to generate current to lead the voltage. The lead current 445 then drives another delta winding 446. This induction motor is also a generator, requiring a starting current to start the generator.

Figure 4c shows another AC generator. The rotor 447 includes magnets 448, 449, 450, 451. Rotor 452 includes rectangular electromagnetic coils 453, 454, 455 to generate three- phase power 456, 457, 458 having a common neutral. The movement of the axle 460 is converted into electricity.

The motor-generator pair of fig. 4d may be used to convert the ac frequency and voltage of the power source 461. The pair shares the induction rotor sheet 462. Below the sheet is the motor stator with two rectangular windings 463, 464 connected by a capacitor 465 to provide a 90 phase advance in 464. The stator windings drive the rotor 462. The current induced in the rotor then induces a current in the 6 delta windings 466, 467, 468, 469, 470, 471 above 462. Winding pairs 466, 469 are connected in series by 472, with a neutral port 473 and the other port producing an AC phase 474. Another AC phase 476 is generated by 475 the connected pairs 467, 470. A third AC phase 478 is generated by 477 connected pairs 468, 471.

The rotor sheet 462 may be redundant because single phase AC in the polygon winding may directly induce three phase AC in the delta winding. The resulting rotor-less transducer is static.

Detailed description of integrated thermal turbine and generator

Figure 5 shows a cross-sectional view of a thermal turbine and generator. The thermal turbine comprises a compressor 501, a heating chamber 502 and an expander 503, wherein the horizontal cross-sectional view is shown on the top and bottom of fig. 5 as two 4-helical disks.

Four compressor screw channels 504, 505, 506, 507 rotate to compress the outside air in. The compressed air then enters the heating chamber 502 from the center of the compressor 501. When the compressor is rotated in one direction (clockwise in the figure), the gas is compressed by flowing in the opposite direction (counterclockwise in the figure) in the compressor helical passage.

For heat generation by gas combustion, combustible gas enters the heating chamber 502 through the fuel nozzle 508, where a fuel-air mixture is ignited.

For heat generation by concentrated solar thermal power, the sunlight is focused in the top center of the expander 513, possibly with a glass top to allow the focused sunlight to enter the chamber.

When a single turbine rotates in one direction, the compressor 501 and the expander 503 rotate in the same clockwise direction. The gas expands in four expander channels 509, 510, 511, 512. The gas rotates in these channels in the opposite direction (counter-clockwise) to the turbine rotation. The gas pressure causes the turbine to rotate clockwise. The pressure-depleted gas is discharged at the periphery of the expander.

The expander screw is tapered with decreasing depth from a greater depth 513 near the center to a lesser depth 514 near the outlet. This taper allows the pressure in the helix to be slowly released.

The compressor screw may be tapered to induce a higher compression ratio. Alternatively, we can stage a stack of multiple compressors, acting alternately as centrifugal and centripetal compressors.

In an alternative embodiment of the compressor, we can use a scroll compressor containing two Archimedes screws as shown in fig. 9 instead of a conical screw compressor. Scroll compressors allow for high gas compression ratios due to the confinement of the gas between the two scroll Archimedes spirals. However, the contact points of the vortex to the spiral of the vortex are abrasive.

The turbine rotates about two ends 515, 516 fixed to the axis of rotation on the turbine housing. We can use ball bearings, air bearings or magnetic bearings for smooth rotation.

Generator 517 is shown on the periphery of the turbine-generator. We place the magnets 518 on the edge of the rotor disk with opposite poles on the top and bottom of the disk as shown.

We use two annular solenoids 519, 520 on the top and bottom of the magnet. The two solenoids may be connected in series to a dual voltage output. The two solenoids may act as magnetic bearings for the turbine. The permanent magnet 518 is levitated by magnetic force from solenoids 519, 520.

The two end portions 521, 522 form the terminals of the DC generator. The external load 523 consumes the generated electric power. Wherein the load controller is operable to control the rotational speed of the turbine. The high voltage increases the rotation speed. A low external load resistance increases the current flow. The large current flow provides a strong torque resistance to the work provided by the thermal turbine.

A thermal turbine may exert work directly on an external mechanical load, such as a gearbox of an automobile or a turboprop of an aircraft. The generated power may be stored via a chemical battery or a super capacitor. The generated DC power is stored without DC to AC reversal. The stored DC power may be retrieved as DC to drive the motor. The electric motor is the same generator as the combined compressor-expander-generator-electric motor shown in fig. 5. We may not need another motor.

Detailed description of air conditioner and dehumidifier

An embodiment of an air conditioner and dehumidifier is shown in figure 6. The top of the figure shows a single rotor of a combination of compressor 601 and expander 602.

We transfer the compressed air down to a heat exchanger 603, which heat exchanger 603 generates gas heat to a water heating tank 604. The cooling of the compressed air causes its moisture to condense in the chamber 605 and collect via 618. Cold water enters at 616 to be heated in the water tank 604. Hot water is extracted at 617.

The cooled compressed air is then further cooled by ambient air passing through conduit 606 to expander 602. The air from the expander 602, which is depleted of pressure, is directed through vent 607. The expander also serves as a blower to deliver cooled and dried air to the rooms in the building.

The compressor is powered by a DC motor 608 of the same construction as the DC generator for the thermal turbine. The rotor magnets 609 are rings having magnetic axes aligned with the rotor axis of rotation. The stator coils 610, 611 are powered by a DC power source 612.

The motor control device 613 controls the motor voltage and current. The voltage controls the rotational speed. The compressor motor is gradually ramped up to the desired compression speed. The current controls the torque force required for compression. The compressor is hinged at 614, 615 to the bearings.

An alternative embodiment decouples the compressor 601 from the expander. The compressed air can be delivered to the individual rooms through thin nylon tubes. An expander is located in each room, delivering cool air and possibly electricity generated by the rotary expander.

This alternative may be used in villages with centralized compressors and generators. The compressor may be powered from solar panels or from a thermal turbine driven by solar heat or gas combustion. Compressed air can also be stored in large quantities for use at night. We delivered compressed air to the cabin through a thin nylon tube rather than through the power of a metal conductor. The compressed air provides cooling and refrigeration for individual households. The expander located in each home can also be integrated with a DC homopolar generator to produce low voltage DC that can be used for LED lighting, television and battery charging.

We also describe a portable embodiment of an air conditioner and dehumidifier. The unit may be placed on the back of a person for cooling and dehumidification. This embodiment is similar to the embodiment of fig. 6 without the heat exchanger 604. The top compressor-expander was placed near the top of the parabola, where the top surface of the parabola blown the cooled air to our back. The bottom condenser collects the compressed air to be cooled, dehumidified, and returned to the expander.

Detailed description of solar Water desalination

Fig. 7 shows a water desalination system that employs solar energy to evaporate brine under reduced pressure. Photovoltaic power 714 may be used to drive compressor 704.

Desalination systems have similar water heating and steam condensing subsystems as used for air conditioning with dehumidification. We compress low pressure steam rather than humid air.

The high water column 701 has a reduced pressure at the water head 702. The brine tank 703 may be made of strengthened glass, reinforced concrete or ceramic materials that are resistant to brine corrosion.

Above the head portion and inside the water tank 703, the compressor 704 is articulated at 712, 713 and driven by the motor 705. The compressor draws low pressure vapor from inlet 715, compressing and heating the vapor. The steam leaving 713 heats the salt-containing water in the tank 703 for further evaporation.

The cooled vapor condenses to water in chamber 707, which may be pumped out through 708.

The circulation of the brine is as follows. The saline water may be preheated before entering the water chamber 703 through the inlet 710. Preheating may be achieved by heat exchange with saline waste. We can preheat the saline water in the solar water heater using the vacuum glass water heating pipe.

Parabolic solar collector 709 focuses the solar energy onto brine column 703. The geometry of the collector is shown in fig. 8. The focused sunlight heats the saline water which rises to the top 716 and largely evaporates with the reduced pressure under the heat of the water. The water is also heated by the condensing steam in the heat exchanger 706.

The concentrated brine migrates to 717, cools due to further evaporation, and sinks to the bottom. The brine waste is discharged at 711. Heat exchange may occur between the hot brine waste and the incoming brine containing water.

To facilitate circulation from the inlet 710 to the outlet 711 through the top locations 716, 717, we may divide the vertical volume of the brine tank into sections. If the brine tank is made of transparent glass, the zone boundaries may also absorb focused sunlight.

The saline water may also be heated by hot air exhaust from a gas powered turbine. This configuration may be used to purify the wastewater produced by fracturing at the well. The combined heat engine and solar water desalination unit can also be a real rescuer of ocean going vessels and stranded island citizens.

Concluding sentence

Human survival has three basic elements: air, water and sunlight. With these three elements, we achieve all human comfort, perhaps with the aid of gaseous fuel as a backup: cooling, heating, food, drinking water and cleaning water, and energy required for communication, calculation and transportation. We believe that the described invention will provide these human comfort where and when needed through personal energy demonstration rather than centralized production.

Sounding: jim Hussey, Ankur Ghosh, Forest Blair and Jerry Jin from Monarch Power implemented and tested early versions of the turbine. Ronan Reynolds of Monarch Power corporation has performed three-dimensional modeling for this patent invention, and has prototype, test and verified the theory proposed in this patent application. Discussion of spiral turbine hydrodynamics was initiated by professor Daniel Bliss at arizona state university, YC Chiew at rogses university, and Falin Chen at taiwan university, china. Keng Hsu by ASU teaches that the 3D laser prints the metal turbine model.

Claims (17)

1. A conical helical gas turbine comprising:

a plurality of spiral passages for gas to flow from the spiral turbine from the center to the periphery; wherein the helical channel comprises:

increasing the radius, so that the radial distance of the gas in the turbine from the center increases along with the angle of the turbine turning;

the section area of the spiral channel is decreased progressively, so that the area of the outer wall in the spiral channel is larger than that of the inner wall;

the spiral channels push the outer wall with a large area due to air pressure, so that the pressure of the air pushes the turbine to rotate.

2. The tapered spiral gas turbine according to claim 1, wherein the hole area decreases linearly with the angle of turn.

3. The tapered spiral gas turbine according to claim 1, wherein the hole area decreases logarithmically with the angle of turning.

4. The tapered spiral gas turbine of claim 1, used as a gas compressor turbine, said gas compressor turbine comprising: a plurality of conical index helical channels through which gas flows from the periphery to the center of the conical helical gas turbine along a relatively large area of the outer wall of the conical index helical channels; the increasing sectional area of the spiral channel reduces the gas velocity, so that the gas pressure gradually increases towards the center.

5. A conical helical gas turbine for converting kinetic energy into electrical energy, said conical helical gas turbine comprising:

a plurality of coaxial disks comprised of annular members having axially oriented permanent magnets of alternating polarity;

wherein each of the plurality of coaxial magnetic disks has a plurality of inductive coil disks comprising a plurality of coaxial polygonal conductor windings, wherein the inductive coil comprises two ends, wherein a first end comprises a phase of the generated energy and a second end comprises a connection to a median line;

wherein kinetic energy is exchanged between the current flowing in the plurality of induction coil discs and the relative rotational movement of the plurality of coaxial magnetic discs and the induction coil discs.

6. The tapered spiral gas turbine of claim 5, further comprising a polygonal induction coil, and a multiphase alternating current induced between the plurality of coaxial disks and the plurality of induction coils, the current driving a current induced by an electric field, wherein the electric field is induced by relative rotational motion that changes the magnitude of magnetic flux flowing from alternating pole coils through the polygonal induction coil.

7. The tapered spiral gas turbine according to claim 5, wherein said plurality of coaxial magnetic disks comprises a single circular conductor disk adapted to provide current mutual inductance between said plurality of coaxial polygonal windings and said circular conductor disk to produce conversion between kinetic energy and electrical energy.

8. The tapered spiral gas turbine according to claim 7, wherein said plurality of generator polygonal windings have different numbers of sides, wherein said plurality of generator polygonal windings are connected in series.

9. The tapered spiral gas turbine as claimed in claim 7, further comprising:

a first set of polygonal windings of the plurality of polygonal windings is driven by an alternating current having a voltage, a frequency and a number of phases to be converted,

a second set of polygonal windings of the plurality of polygonal windings, the second set comprising a different number of sides and turns than the first set,

wherein the first set is induced directly on the second set, the first and second sets being connected in series.

10. The conical helical gas turbine according to any one of claims 1 to 4, for use as a heat engine powered by pressurized gas, comprising:

a gas compressor turbine producing pressurized gas;

a central heating chamber receiving pressurized gas and heating the pressurized gas in the chamber;

and the pressurized heating gas is discharged from the central heating chamber along the conical exponential spiral channel of the turbine to push the turbine to rotate, so that the turbine is used as a heat engine.

11. The tapered helical gas turbine according to any one of claims 1 to 4, for use as a refrigeration device for refrigeration by compressed gas, the refrigeration device comprising a plurality of tapered exponential helical channels for use as gas compressor turbines for pressurizing gas from the periphery to the center via the inside of the turbine; a central chamber for extracting thermal energy generated by the pressurized gas, thereby cooling the pressurized gas; a gas expansion turbine, said cooled pressurized gas being passed along a plurality of conical exponential spiral channels, to depressurize the gas from the turbine from the center to the periphery, to cool the gas, as a refrigeration means.

12. The refrigeration unit of claim 11, further generating hot water from the heat energy drawn from the central chamber, such that the refrigeration unit can simultaneously supply hot water.

13. The refrigeration unit of claim 11, further comprising means for generating potable water drawn from said gas containing moisture, whereby cooling of the pressurized gas through the central chamber causes the moisture in the gas to condense into potable water as the means for generating potable water.

14. The refrigeration unit of claim 11, further comprising cooling said pressurized gas by injecting moisture into said central chamber, whereby said moisture evaporates, and depressurizing and cooling said cooled compressed gas in said gas expansion turbine.

15. The conical helical gas turbine according to any one of claims 1 to 4, for use as a solar water purification device, comprising:

the water heater is used for heating the purified water by solar energy;

a water column for evaporating the purified water heated by the water heater, wherein the boiling point of the purified water is reduced due to the pressure reduction of the water column head, and low-pressure water vapor is generated in the column;

a gas compressor turbine that pressurizes the low pressure steam to condense the steam into purified water; a water vapor condensation chamber for collecting and pumping away condensed purified water;

and the heat exchanger is used for exchanging the heat energy generated by the condensation of the water vapor to the purified water in the water column so as to evaporate more purified water.

16. Solar water purification apparatus according to claim 15, wherein said water heater includes a reflective surface adapted to focus solar energy onto said water column surface.

17. Solar water purification apparatus according to claim 15, wherein said water heater is a conventional solar water heater using vacuum heat absorption tubes for absorbing solar heat to heat water in the tubes to produce hot water to evaporate purified water in said column.

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