System for cleaning gases and sequestration of particulate material from internal combustion engines with conversion of waste into extra energy

Abstract

A fluid cleaning and filtering system includes a pre-treatment system before a force generation turbine to condense and pretreat gases and particulate matter; a flow rectifier before a tangential inlet; diffuser pipes for compressing the gases and particulate matter therein and project same into the deflector disks, diffuser pipes at an outlet of the so-called condenser, a purger, a diffuser and a deflector; a force generation turbine; an energy generator using torque from the turbine rotor; an internal energy generator; a flow rectifier in a first tangential inlet and a flow rectifier in a second tangential inlet; a new full-cone atomizer nozzle to wet particles and clean gases; a diffuser in the condensers and a deflector disk for the condensers.

Claims

1. A fluid cleaning and filtering device, comprising: a torque generating turbine housed into a U-shaped shell, wherein the turbine has an input fluidly connected to a flow rectifier, and an output fluidly connected to a dispenser; an inner generator within the turbine housing connected to the turbine, such that said turbine provides mechanical energy to said generator; labyrinths connected to flanged retainer boxes that are arranged in each generator end, configured to prevent the gas and particle flow to within the generator; at least one disintegrating turbine; wherein at least one disintegrating turbine each has an input and an output; a rotor connected to at least one disintegrating turbine; and at least one outer generator outside the turbine housing.

2. A method of cleaning and filtering fluid, comprising the steps of: performing a first cleaning and filtering of the fluid; injecting the fluid into a turbine for a second cleaning, wherein a movement of the turbine drives an inner generator within the turbine housing and an outer generator outside the turbine housing; dispensing the fluid from a dispenser; performing a third cleaning; injecting the fluid in at least one disintegrating turbine for an additional cleaning; and flowing fluid to a collection reservoir.

3. A fluid cleaning and filtering device for cleaning and filtering fluid according to a method of claim 2, comprising: a diffuser-baffle-condenser-purger (DDCP), including a pre-condenser with an expansion chamber promoting the compression and posterior expansion having at least one atomizer nozzle arranged in an end thereof wherein a flow rectifier is in contact with the pre-condenser; a cylindrical device with baffle disks in an inner part thereof and diffuser pipes in an outer part thereof, wherein said cylindrical device has at least one atomizer nozzle arranged along a 1 length thereof, and wherein radial pipes pierce the baffles and the diffusers; and a fluid compressing conical output arranged at an end of the cylindrical device; wherein the conical output is connected to a pressure concentrating flow rectifier.

Description

BRIEF DESCRIPTION OF DRAWINGS

(1) The invention will be described below, with reference to the accompanying drawings given by way of example of one of the possible embodiments of the proposed solution and in which:

(2) FIG. 1 represents a simple flowchart of the means involved in establishing the device and implementing the filtering and cleaning method of exhaust gases of an internal combustion engine;

(3) FIG. 2 represents in enlarged scale a longitudinal diametrical view through the pre-treatment and homogenizer of the exhaust gases received from the engine for humidification and cooling;

(4) FIG. 3 represents in enlarged scale and in a manner somewhat simplified an axial view of a pair of means of treatment and the exhausting means of the device in question, to provide the final humidification of the exhaust gas flow, the shearing of solid particles contained in said flow and compression of the latter and further the impulse of the exhaust gas flow, means of treatment to the condenser means;

(5) FIG. 4 represents a diametrical sectional view of a treatment means, said section having been taken along line IV-IV in FIGS. 1 and 3;

(6) FIG. 5 represents in enlarged scale and in a somewhat simplified longitudinal axial view a condenser means and collection tank;

(7) FIG. 6 is a cross-sectional diametrical view, somewhat simplified, of the exhaust and condenser means, said section being taken along line VI-VI in FIG. 1;

(8) FIG. 7 represents an enlarged longitudinal view of the means of gas liberation arranged downstream of the condenser means.

(9) FIG. 8 represents a simple view of the dynamic flowchart in random order and a demonstration of the equipment and technological innovations including: innovation 1, innovation 2, innovation 3 (IN1, IN2, IN3). It also presents condensers diffusers and baffles after the force turbine coming from the fourth stage (called Force Generator Turbine or simply TGEF);

(10) FIG. 9 represents a view in sectional elevation of the gas flow and particulate material coming from the combustion and passing through the TGEF;

(11) FIG. 10 represents a side elevation of the complete system.

(12) FIG. 11 represents a sectional view in elevation with details of operation, including atomizing nozzles, gas and particulates input in tangential geometry, heat sinks, diffuser pipes and baffles.

(13) FIG. 12, IN1, represents a longitudinal view of part of technological innovations: disintegrating turbines, now working with central input or centrifuge with input and output of gases and tangential PM (particulate material) and new Inner Energy Generator (GIE), producing DC and AC.

(14) FIG. 13, IN2, represents a longitudinal view of the new process of treating gases, positioned after the TGEF. It comprises: pre-condensers, diffusers, baffles and purgers stabilizing and increasing the efficiency of the TGEF, curved inlet and tangential outlets. The IN2 works both vertically and horizontally (taking into account that there will be changes in purgers, atomizing nozzles and inputs, in case it works vertically).

(15) FIG. 14 represents a more detailed view of the condenser diffuser I, presented together with the diffuser and condenser II in FIG. 13.

(16) FIG. 15 represents a more detailed view of the condenser diffuser II, presented in together with the diffuser and condenser I in FIG. 13.

(17) FIG. 16 represents in a longitudinal view a filtering system comprising: feeding pump of atomizing nozzles, screened baffle, level, inlet and outlet of waste supply and discharge.

(18) FIG. 17 represents in a longitudinal view the Force Generator Turbine: we can apply the TGEF near the distributor where we will have a better use of the heat resulting from combustion, a more indicated location to the “Y”. It is also possible that the Y is also in the exhaust pipe end of the fourth stage, where temperatures at about 200° C. prevail. FIG. 17 consists of: a rotor, “U” rotor shell to better use friction, generate more force, with flanges input and output with flow rectifier, bearing housing, conventional bearings as needed or magnetic bearings, a labyrinth preventing leakage of the gases subjected to very high pressures, acrylic seals or as needed and drive shaft coupled to the rotor generating power to feed the external generators and the new Inner Energy Generator.

(19) FIG. 18 represents a sectional side view of the items mentioned in FIG. 17.

DESCRIPTION OF THE INVENTION

(20) As illustrated in the drawings, the filtering and cleaning device for the exhaust gases and particulate materials simultaneously with co-generation of electricity initially comprises means of pre-treatment 10 to pre-humidify and pre-cool the flow of hot gases, released by the internal combustion engine at temperatures ranging generally in the range of about 350° C. to about 650° C.

(21) The means of pre-treatment 10 (see FIG. 2) comprises a tubular portion 11 having an inlet end 11a connected to the discharge of the engine, an output end lib, and an atomizer means 12 mounted internally to the tubular portion 11 and arranged to atomize water in the exhaust gas flow received from the engine, with said atomization made in the same direction as the exhaust gas flow.

(22) In this first step of the method of filtering and cleaning of the exhaust gases, the gas flow has the particulate material pre-humidified and all the mass thereof pre-cooled as a function of water atomization, allowing not only the increase of density of particulate material in the exhaust flow, but also the cooling of the latter to a temperature of about 65° C. to about 95° C. lower than the temperature of the incoming gas flow in the device in question.

(23) Water to be atomized in the exhaust gas flow is pumped from a water source 20 (see FIG. 4) which may take different forms, as described later. One form is represented by a tank 21 mounted in the automotive vehicle in which the device in question is installed or any support to the mounting site.

(24) The flow of exhaust gases, already pre-humidified and pre-cooled, is then fed to a flow homogenizer means 30 (referred to in FIG. 4 and detailed in FIG. 2) which is constructed for swirling the exhaust gas flow, causing homogenization.

(25) In the illustrated construction, the flow homogenizer means 30 comprises an annular tubular body 31 (see FIG. 2) defined by an outer tubular wall 32 and an inner tubular wall 33, which define together with end walls 34a, 34b, an outer annular chamber CE with ends closed by end walls 34a, 34b, and an inner cylindrical chamber CI with an end closed by one of the end walls 34a and the other end open and defining an outlet nozzle 30b of the flow homogenizer means 30, which inlet nozzle 30a is provided substantially radially through the outer tubular wall 32.

(26) The inlet nozzle 30a of the flow homogenizer means 30 may take the form of a volute, to easy the admission of the exhaust gas flow into the outer annular chamber CE, filling and pressurizing the latter and being then divided into multiple radial gas flows which are passed through a plurality of radial pipes 35 arranged through the inner tubular wall 33 and open to the outer annular chamber CE and for the inner cylinder chamber CI.

(27) The construction of the flow homogenizer means 30 is made to cause within the inner cylindrical chamber CI of the annular tubular body 31, a strong swirl of multiple exhaust gas flows passing through the plurality of radial pipes 35, causing a high degree of homogenization of the mass of particulate material suspended in the exhaust gas flow already pre-humidified and pre-cooled. The internal cylindrical chamber CI of the annular tubular body 31 thus defines in its interior a swirling and homogenization region of the exhaust gas flow, said inner cylindrical chamber CI open to the output nozzle 30b of the flow homogenizer means 30, which nozzle is open for at least one expansion region 36, to which the already swirled and homogenized gas flow is directed.

(28) The exhaust gas flow already pre-humidified, pre-cooled and homogenate is then conducted, the expansion region 36, usually in the form of a cross section of pipe length not less than that of the inner cylindrical chamber CI to at least one treatment means 40 (see FIG. 4), which is designed to provide a final humidification with water of the flow of exhaust gases, shearing of solid particles and further their compression to a pressure of about 1.2 times the discharge pressure of the engine.

(29) In the illustrated construction, there are provided two treating means 40, arranged in parallel, each receiving a respective portion of the exhaust gas flow released through the homogenizer means 30 through a respective expansion region 36.

(30) Each treatment means 40 comprises at least one rotary compressor 41, with a rotor R having a horizontal axis 44 and multiple compression stages, concentric and maintained in radial fluid communication with each other and disposed within a tubular shell 42 provided with a radial inlet 42a generally lower for the flow of exhaust gases, already homogenate and received from the respective expansion region 36 of the flow homogenizer means 30, and a central axial outlet 42b (see FIG. 3) to release the flow gas with the particles already sheared, humidified and cooled together with the gas mass.

(31) Also according to the exemplary construction illustrated in the drawings, each stage E of rotor R (see FIG. 4) of the rotary compressor 41 is defined between two cylindrical walls 45, concentric with said stage, wherein said stages E take the form of concentric annular chambers, having the ends of the cylindrical walls 45 respectively fixed to end walls 46 (see FIG. 3) of rotor R, which close the ends of stages E.

(32) Each treatment means 40 (see FIG. 4) is constructed to provide a humidification of the exhaust gas flow. For that, within the tubular shell 42 of each compressor 41 there is provided an atomizer means 43 for water, usually an atomizer nozzle arranged in the upper region of the tubular shell 42, preferably within a radial tubular projection 42c of the latter opposite the radial inlet 42a of the tubular shell 42.

(33) According to this construction, each rotary compressor 41 carries, externally to the cylindrical wall 45, external to the first compression stage E a plurality of small radial blades 47, arranged to conduct when the rotary compressor 41 rotates, water humidification, sprayed within the tubular shell 42 by the atomizer means 43 contained in the reservoir 43, into the first compression stage E through radial holes 45a provided in said outer cylindrical wall 45 of the first stage compression E. It should be noted that the fluid communication between the compression stages E between the last compression stage E and the central axial outlet 42b of the tubular shell 42 is defined by a plurality of radial holes 45a provided in the cylindrical side walls 45 that limit each compression stage E. The radial holes 45a are arranged offset each other every two adjacent compression stages E.

(34) Thus, each rotary compressor 41 has the multi-stage tubular chambers in the form of annular, concentric and radially adjacent to one another chambers, having the ends closed by end walls 46 (see FIG. 3) of the rotor R.

(35) Also according to the construction suggested in the accompanying drawings, each rotor R of a rotary compressor 41 further comprises, at least in part of different compression stages E a plurality of shear rods 48 (see FIG. 4) arranged axially, angularly spaced apart and ends fixed opposite the respective end walls 46 (see FIG. 3) of the rotor R, said rods shear 46 rotating together with the rotor R, so as to come into collision with the solid particles contained in the flow of exhaust gases.

(36) The device in question further comprises a flow rectifier pipe 49 disposed coaxially to the rotary compressor 41 and interconnecting its central axial outlet 42b to the radial exhaust means 50.

(37) With the constructive arrangement described above for each treatment means 40, 41 the two rotary compressors are mounted in parallel and coaxial with its central axial outputs 42b and converging toward each other. In this construction, the flow of exhaust gases received within the tubular shell 42 is swirled, humidified intensely by mixing with atomized humidification water to the interior of the tubular shell and led through the various stages of compression E when the small radial blades 47 rotate, the gas flow being progressively compressed, passing the first compression stage E, through the radial holes 45a provided on the outermost cylindrical side wall 45 of the rotor R. Thus, the flow of exhaust gases is progressively compressed and humidified, from one stage E to the next, radially innermost, while the solid particles are progressively sheared by shearing rods 48 disposed within each compression stage E. At the end of the compression stages E, the flow of combustion gases, already fully humidified and with its suspended solids already intensely sheared, is released through the central axial outlet 42b and directed to a radial exhaust means 50 disposed generally coaxially to the rotary compressors 41.

(38) According to the illustrated construction, the radial exhaust means 50 (see FIG. 6) comprises a cylindrical housing 52 with opposite ends of each attached to a tubular shell 42 of a respective treatment means 40 and housing a rotor RE mounted on the same shaft 44 of the rotors R of the compressor 44 and having, at each end, a central axial inlet 52a (see FIG. 3) to the exhaust gas flow from each treatment means 40 and a plurality of radial fins 55 (see FIG. 6), wherein the cylindrical shell 52 opens laterally to a side volute 53 that defines a lower outlet 54 for the water and exhaust gas containing water vapor and suspended solid particles. As can be seen from FIGS. 3 and 6, the exhaust flow containing water vapor and solid particles is then fed to a condenser means 60 comprising an inlet chamber CEN (see FIG. 1), of elongate tubular annular shape with closed ends arranged horizontally and receives, medially and tangentially, the exhaust gas flow released from the lower outlet 54 through the exhaust means 50.

(39) Internally, the inlet chamber CEN, the condenser means 60 comprises a outer chamber CEX, also elongated tubular annular, horizontally arranged and defined between an outer tubular wall 62, separating the same from the inlet chamber CEN, and an inner tubular wall 63, said outer chamber CEX being closed by an end wall 64 at one of its ends.

(40) The exhaust gas flow admitted to the inlet chamber CEN pressurizes the interior of the latter and is passed to one of the end regions of outer chamber CEX, through a plurality of windows 65 provided in the outer tubular wall 62. In said end region of outer chamber CEX radially aligned with the windows 65, an annular atomization chamber CAT is formed (see FIG. 6), which is separated from the outer chamber CEX by an annular partition 66/66a which is pierced by a plurality of eccentric axial pipes 67 communicating the annular chamber with the atomizing annular chamber CAT with the outer chamber CEX. In the end wall 64 common to the annular atomizing chamber CAT and external chamber CEX, atomizing nozzles 68 are mounted for atomizing water tank 21 into the exhaust gas flow that enters the annular atomization chamber CAT, and the atomization performed in the axial direction facing the eccentric axial pipes 67.

(41) The inlet chamber CEN is inferiorly provided in its region adjacent to the windows 65 of the annular atomization chamber CAT, a lower outlet 65a which is connected by a conduct 65b, to the collection tank 70, to drive, gravitationally, water, condensate and particulate material already released radially and inferiorly of the annular atomization chamber CAT.

(42) The inner tubular wall 63 limits in its interior the inner chamber CIN of tubular shape having an open end to an adjacent end of the outer chamber CEX and the opposite end projecting through the annular atomizing chamber CAT out of the condenser means 60, to be open to the atmosphere or further preferably connected to an exhaust means 100.

(43) The outer chamber is further provided with a plurality of annular partition walls 66a, arranged parallel and spaced from each other transversely to the longitudinal geometric axis of the outer chamber CEX. The partition walls ring 66a define, between them, annular chambers CA held in communication with a plurality of axial pipes 67 disposed through the annular partition walls 66a and radially remaining spaced from the inner 63 and outer 62 tubular walls of the outer chamber CEX and having the ends open and projecting inwardly the respective annular chambers CA, wherein the axial pipes 67a of an annular partition wall 66a axially offset relative to axial pipes 67a of the two adjacent annular partition walls 66a.

(44) With the construction proposed for the means condenser 60, the gas flow, still containing water vapor and remaining particulate material, is passed by the annular chambers CA, progressively condensed and released through the open end of the outer chamber CEX, to a device for breaking droplets 80, provided with a lower outlet 81 connected to a pipe 82 which leads the condensate and particulate material suspended therein to the collection reservoir 70.

(45) The remaining gas flow, already cooled and cleaned, can be released to the atmosphere or further preferably conducted by CIN internal chamber to the exhaust means 100.

(46) It should be noted that the water to be atomized in pre-treatment means 10, treatment means 40 and condenser means 60 is pumped from the water source 20 that, in the illustrated example, is defined by the tank 21. The pumping can be done by any suitable pump 25 and through pipes 26.

(47) The collection reservoir 70 may be constructed in different ways, with or without a means 71 for treating collected water and condensate, for example, by filtration so that the water used in the process is reused in a closed loop, that is, returned to tank 21. This arrangement allows for a great saving of water to be used in the humidification method, without requiring continuous water replenishment in the tank 21, increasing the autonomy of the device, particularly when applied in automotive vehicles.

(48) The means of exhaust 100, when provided, is coupled to the output of inner chamber CIN of the condenser means 60 for receiving the cooled and purified gas flow in the latter and subjecting it to an additional condensation operation, with the main objective of collecting any remaining water in vapor form in the exhaust flow.

(49) In the illustrated construction, the gas flow leaving the condenser means 60 is led through a proper pipe 69 (see FIG. 1), the exhaust means 100 which may take the form of a tubular body 101 arranged vertically, and a lower end 101a connected to the pipe 69 and an upper end open to the atmosphere. In its middle region, the tubular body 101 houses a plurality of annular trays 102, horizontal and somewhat spaced apart, through which the ascending gas flow is passed and the peripheral regions of the annular trays 102 projecting and open to the inside of the collection chamber 103 surrounding the tubular body 101 and having an annular bottom wall 103a from which a drain pipe 104 protrudes downwards having an lower end open into the pre-treatment means 10 downstream the atomizing means 12 and upstream the flow homogenizer means 30. The junction of the drain pipe 104 with the tubular portion 11 of the pre-treatment means 10 is made so that the through-flow of exhaust gas by the latter operates as a ejector producing a pressure drop inside the drain pipe 104 and the consequent aspiration back to the device of any condensate captured within the collection chamber 103, preventing the loss of water used in the process of filtering and cleaning the exhaust gases.

(50) With the proposed construction to the exhaust means 100, the gas flow from the condenser means 60 is passed through the interior of the annular tray 102, in which the remaining vapor water is condensed and radially conducted to the collecting chamber 103 and aspirated back by gravity and pressurized to the pre-treatment means 10. The filter flow 105, usually in a cartridge shape to be periodically replaced, treat the remaining gases so they can be then released to the atmosphere.

(51) Details of Innovation or Strategic Changes in the Layout:

(52) As can be see in FIG. 8, the box coupled to the labyrinth formed internally with seals prevents the passage of water into the Inner Energy Generator (GIE) engine 132. The GIE is composed of a tangential entry of gaseous and particulate provided from the primary treatment phase of gases and particulate material 129. The pre-treatment 129 is performed by a properly designed device for the purpose of causing a compression and decompression, new expansion 121 and coupling measurements 107.

(53) For pre-treatment, there are included a rectifier flow before the tangential inlet 130. In order to compress gases and particulates therein and throw them in the baffle disk 111, the diffuser pipes in the output of the more complete and efficient condenser, purger, diffuser, baffle (CPDD) 110, heat sinkers, the core cooling of condenser, diffuser and baffle 108, the condenser sink 112, the expansion chamber and conical output 128.

(54) Many improvements and innovations were added, including: the inlet flow rectifier in force generating turbine 109, the inflow from the diffuser condenser to the generator turbine/rotor 119, the output of gases and particulate material to flow to the distributor, condenser I and II 113, the distributor, feeding the condenser I and II 135, piping, feeding the condenser I in its second stage 131, the conical pipe dimensioned to direct flow and curve for the condenser II 120, the curved flange, feeding the rectifier flow with tangential input I 114, the rectifier flow with a tangential entry into the condenser I, called tangential inlet I 127, the flow rectifier of the tangential inlet to the condenser II, called tangential inlet II 134

(55) Also the model of the full cone atomizer nozzle has evolved for hydrating particles and cleaning gases 115. Such improvements include: the shape of the diffuser condenser II 133, the baffle disk of the condenser II 116, piping and curve with the flow toward disintegrating and cleaning turbine of Gases, particle collection and co-generation of energy (TDGE), input II 126, the snail with tangential input into the condenser I 125, the pipe interconnecting the condenser to the TDGE, input I 122, the pipe interconnecting the condenser II to the TDGE and the inlet II 145.

(56) Other improvements developed in the system include the low, middle and high power generator, taking advantage of rotor torque, internal co-generation antimagnetic type energy, using neodymium or conventional 117, the magnetic generator in series, according to the power the motor and the rotor 124. Other developments including the use of conventional or magnetic bearings of high quality to avoid friction. Also we work at the maximum within the inertia 123, shell/closing box of the rotor lock/force generator turbine 141, the rotor blades in the force generating turbine 118, the intermediate rotor between the turbines in order to expel dried and purified gases, free of particles into the atmosphere 142, the shell of the intermediate rotor of the turbine, closing of 142, the pipe I with the purpose of draining waste water with disintegrating turbine to the water tank 143, pipe II in order to drain waste water with disintegrating turbine to the water tank 140.

(57) Also the flanged labyrinth prevents the contact of gases and particles between the two disintegrating turbines 144 (left side), the flanged labyrinth preventing the contact of gas and particles between the two disintegrating turbine 138 (right side), the flange and acrylic retaining/sealing box 132, the disintegrating turbine 137, comprising: cylinders, tracks, contact cell, rods separating gas and waste water, in order to pass gas to the core of the turbine and waste water to the water tank.

(58) Additionally, there have also been developed the fourth manifold temperature stage at approximately 800° C., which can vary for more or less, the flow direction of condenser/diffuser/baffle 106, the flow rectifier 136, the screened baffle with direct flow of waste water and return of cleaned gas into the atmosphere 146 and 146a. Each mentioned-above item is an important detail to increase the intensity of power generation and the treatment efficiency of each gaseous pollutant and microparticulates.