WO2018132640A1 - Procédé et appareil pour chauffer et purifier des liquides - Google Patents

Procédé et appareil pour chauffer et purifier des liquides Download PDF

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Publication number
WO2018132640A1
WO2018132640A1 PCT/US2018/013454 US2018013454W WO2018132640A1 WO 2018132640 A1 WO2018132640 A1 WO 2018132640A1 US 2018013454 W US2018013454 W US 2018013454W WO 2018132640 A1 WO2018132640 A1 WO 2018132640A1
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WO
WIPO (PCT)
Prior art keywords
fluid
cavitation
external rotor
housing
zone
Prior art date
Application number
PCT/US2018/013454
Other languages
English (en)
Inventor
Radovan Hrinda
Douglas S. HIRSH
Original Assignee
US Intercorp LLC
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from US15/405,660 external-priority patent/US20170130954A1/en
Priority to SG11201906491QA priority Critical patent/SG11201906491QA/en
Priority to MX2019008332A priority patent/MX2019008332A/es
Priority to RU2019125132A priority patent/RU2752504C2/ru
Priority to KR1020197023653A priority patent/KR102490810B1/ko
Priority to EP18738867.3A priority patent/EP3568649A4/fr
Application filed by US Intercorp LLC filed Critical US Intercorp LLC
Priority to MYPI2019003991A priority patent/MY195794A/en
Priority to JP2019558991A priority patent/JP7152417B2/ja
Priority to CA3050252A priority patent/CA3050252A1/fr
Priority to AU2018207118A priority patent/AU2018207118B2/en
Priority to BR112019014380-7A priority patent/BR112019014380B1/pt
Priority to CN201880011930.3A priority patent/CN110637193B/zh
Publication of WO2018132640A1 publication Critical patent/WO2018132640A1/fr
Priority to IL267988A priority patent/IL267988B2/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B3/00—Other methods of steam generation; Steam boilers not provided for in other groups of this subclass
    • F22B3/06—Other methods of steam generation; Steam boilers not provided for in other groups of this subclass by transformation of mechanical, e.g. kinetic, energy into heat energy
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24V—COLLECTION, PRODUCTION OR USE OF HEAT NOT OTHERWISE PROVIDED FOR
    • F24V40/00—Production or use of heat resulting from internal friction of moving fluids or from friction between fluids and moving bodies
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24V—COLLECTION, PRODUCTION OR USE OF HEAT NOT OTHERWISE PROVIDED FOR
    • F24V40/00—Production or use of heat resulting from internal friction of moving fluids or from friction between fluids and moving bodies
    • F24V40/10—Production or use of heat resulting from internal friction of moving fluids or from friction between fluids and moving bodies the fluid passing through restriction means

Definitions

  • the invention relates to a cavitation equipment producing heated or cooled liquids, containing at least one engine, a house, the liquid to be heated, and cavernous bod iesrotating in the liquid to be heated, and driven by an external engine.
  • Cavitational devices are also described in United States Patent Nos. 5,188,090 and 5,385,298 to Griggs.
  • a cylindrical body is placed into the housing of the device, and a cloak is provided with cavitational bores.
  • the liquid to be heated is placed into the cylindrical free space between the rotating body with cavitational bores and the internal cloak of the housing; the pressure and temperature of the liquid increases while the cavitational body is rotating.
  • the Griggs patents are incorporated by reference herein in their entirety.
  • the prior art systems described above have a number of disadvantages, including being inefficient and generating noise, primarily due to these concepts addressing the cavitation process as a two dimensional process.
  • One aim of the invention is to eliminate the disadvantages of the known solutions and the harmful cavitational effects in cavitation devices, to eliminate destructive forces internal to the cavitation process, to improve efficiency, and to reduce cavitation noise through a three dimensional vector approach.
  • One object of the invention is a cavitation apparatus producing heated liquids sufficient for fluid purification and alternative methods of heat transfer, containing at least one engine, a housing, liquid to be heated, and one or more cavernous cavitation bodies rotating in the liquid to be heated and driven by the engine.
  • the invention includes the procedure for the operation of the equipment
  • the solution according to the invention advantageously eliminates the otherwise harmful and eroding features of cavitation, while using the generated cavitation bubbles to change the thermal conditions of liquids, primarily water, for water purification, HVAC applications, and other similar processes that require heat transfer.
  • the invention is characterized in that a constricting form is installed in the housing, the constricting form contains cavitation steps, directional & bounce bumpers, and a free constricting gap funnel for the liquid to be heated between the constricting form and the cavitation body (2) allowing for velocity and directional control of formed cavitation bubbles critical for process integrity and reduction/elimination of the destructive forces associated with the cavitation process.
  • the method for the use of the cavitation equipment forms also part of the invention, as intergral components of the overall cavitation system enhance noise reduction, and process efficency.
  • Figure 1 shows a perspective and exploded view of one embodiment of the invention.
  • Figure 2 shows a top of the apparatus of Figure 1 with portions cut away to show detail.
  • Figure 3 shows a sectional view along the line III of Figure 2.
  • Figure 4 shows an enlarged portion of the sectional view in Figure 3.
  • Figure 5 shows an even more enlarged view of a portion of Figure 4.
  • Figure 6 shows discharge locations, and cavitation bore locations with respect to motor speed and calculated fluid velocity at discharge in a standard two dimensional fashion
  • Figure 7 shows a typical cylindrical fluid path within a cavitation head in the third dimension.
  • Figure 8 shows general locations of bumpers with respect to each other to provide for uniform discharge velocity of fluid to cavitation bores in the third dimension.
  • Figure 8A shows a cross section of Figure 8 at the entry point of discharge tunnels
  • Figure 8B shows a cross section of Figure 8 towards the discharge tunnels
  • Figure 9 shows a table of water physical characteristics that vary over temperature change that require velocity control of cavitation process
  • Figure 10 shows overall system requirements to produce a controlled three dimensional cavitation process without negative destructive forces.
  • Cavitational vacuum bubbles are created in the lower pressure parts of liquids, primarily in areas the liquid flows at high speeds. The phenomenon is common in central pumps and in the proximity of ship propellers or water turbines, and may extensively erode the rotating propellers and the surface of all materials affected.
  • the phenomenon is accompanied by vibration and knocking-like noise; it distorts the flow pattern, and reduces the efficiency of the associated engine. Irrespective of the material the propeller or turbine blade is made of, cavitation erodes the respective surfaces by literally eating away even the hardest alloys and creating tiny holes and cavities on the surface. The name of the phenomenon is of mis origin, as cavitation means the creation of cavities. For the above reasons, cavitation is usually a phenomenon to be eliminated.
  • Cavitational vacuum bubbles are generally small, just a few millimeters in size, and the bubbles are generated by a sudden decrease in pressure in high-speed liquid flows between the molecules of the liquid.
  • the bubbles crash when entering high-pressure areas, or explode and fill the space evenly with drops, if the pressure of high- pressure liquids drops suddenly. Small cavities are created among the drops and drop molecules, creating literally vacuum bubbles.
  • the subsequent crash of such vacuum bubbles is accompanied by a low crashing noise and light emission.
  • the crashing of large quantities of liquid molecules produces cracking, bouncing, and rumbling noise.
  • Cavitation is generally a detrimental phenomenon due to it's destructive
  • an improved cavitational apparatus can be made by installing a constriction or interference between a rotating cavitational body and the internal surface of a housing containing the body and, optionally, the internal surface of the rotating cavitational body and a secondary and stationary rotor head. In this case, it is ensured that the vacuum bubbles are continuously exploded.
  • the internal of the housing with the interference or constriction, the liquid to be heated surrounds the vacuum bubbles in the bores upon explosion, cavitational noise can be reduced, and die harmful effects of cavitation can be reduced or eliminated.
  • the invention in one aspect is a cavitation apparatus producing heated purified liquids, containing at least one engine, a housing, the liquid to be heated, a rotating cavitation body rotating in the liquid to be heated and driven by the engine.
  • the engine may be an electric engine, but steam or internal combustion engines, or the rotating shafts of turbines may also be used to drive the cavitation equipment
  • a stationary rotor head can be placed inside of the rotating cavitation body to form the second liquid heating zone.
  • the invention also includes the method for the operation of the apparatus, which entails broadly supply a fluid, for example water to the apparatus for cavitation purposes and subsequent use of the heated fluid as would be known in die art. While water is a desired fluid, the apparatus can be used to heat and purify any fluid if so desired.
  • the advantages of the invention are amplified by having cavitation bores in the rotating cavitational body and the rotor head, if present
  • its external surface is fitted with cavitational bores, much like found in the Griggs patents.
  • the bores and the chamber between the rotating cavitational body and the surrounding housing forms a cavitational flow zone.
  • the external surface of the rotor head is also fitted with cavitation bores so as to face an inner surface of the rotating cavitational body, which is then generally ring-shaped. This creates an additional liquid cavitational flow zone between the inside of the rotating cavitational body and the rotor head to enhance the cavitation of the fluid.
  • the apparatus is designated by the reference numeral 10 and includes an external motor 1 is used to rotate a rotating cavitational body or external rotor 5 through a direct drive shaft 3 that includes a shaft seal 7.
  • the shaft 3 extends through an opening 6 in an end 8 of a housing 9 and an opening 12 in the external rotor 6 5.
  • the external rotor 5 can be rotated at any number of speeds and this depends on the viscosity of the fluid being heated. Typical speeds are from 2500-4000 rpm to generate optimal cavitation of fluid, such speeds similar to those disclosed in the Griggs patents.
  • the motor speed is tuned to the apparatus 10 by use of a variable speed controller 301 along with the directional and bounce bumpers. This is crucial to producing the exact shaft speed S v , that determines horizontal Vx.verticle Vy, and terciary velocity Vz of the fluid at discharge zones 31 , 35 of appartus 10.
  • the fluid is compressed within the discharge funnel, directed, and released at a specific velocity Fv which is determined by the phyiscal arc lenght LA between cavitation zones ( Figure 6) in determining the actual number of cavitation discharge zones with a given cavititation head at any particular motor speed. Since the velocity of the fluid Fv can be tuned, a determination of the time a fluid molecule will take to travel along path LA can be made and the horizontal and vertical component of the fluid at discharge zones 31, 35 can be calculated.
  • tertiary velocity is Vz - dz/ dt
  • the directional and bouce bumpers are designed to drive the tertiary velocity V z to zero, by eliminating the dz component and thus by solving for dx and dy, the location of the cavitation bores 33, 37 and the distance between the bores BA with respect to time (i.e. motor speed) for tuning can be determined
  • Figure 6 only depicts two cavitation bores but it should be understoond that the cavitation bores would extend along the circumference of the external rotor as shown in Figure 3.
  • a rotor housing 9 is provided that has no internal bearings.
  • the existence of internal bearings is a critical failure mode of the Fabian patent as in this design, the bearings would be directly affected by thermal transfer of fluid to bearings during the cavitation process.
  • the shaft 3 of the motor 1 extends through the housing 9 and supports the external rotor 5 for rotation in a cantilevered configuration.
  • the motor has a longer shaft 3 than normal and internal bearings in the motor to support the balanced external rotor 5 when the shaft 3 extends through housing 4- 9.
  • the housing 9 forms a cavity 11 , with the cavity shaped to receive the exteafmal rotor 5.
  • a conventional shaft seal (not shown) is positioned between the motor shaft 3 and the housing 9 for sealing purposes.
  • fluid e.g., water
  • fluid is introduced into the cavity 11 at a rate based upon optimal tuned speed of motor for the fluid during operation of the apparatus 10.
  • an outer surface 13 of the external rotor S faces an inner surface 15 of the housing 9.
  • a gap 17 exists between these two surface 13 and IS, and this gap 17 becomes one fluid heating zone for the apparatus 10, consisting of three lateral cavitation zones 2 IS.
  • six fluid heating zones exist by reason of three sets of three discharge zones 31 and 35 for heating zone 17 and the same arrangement for heating zone 25, so that there are a total of eigtheen cavitation zones 215.
  • This number can be increased or decreased by varying the size of the cavitation head for additional arc length LA consistent with the motor speeds selected.
  • This is accomplished by providing a secondary rotor head 19 in a specific rotational pitch or configuration and has similar physical characteristics as the external rotor 5 to enhance the energy in the fluid.
  • An outer surface 21 of the rotor head 19 faces an inner surface 23 of the external rotor S, with a gap existing therebetween. The gap forms the-another fluid heating zone 25 of the apparatus 10.
  • a housing cover 27 is also provided.
  • the housing cover 27 mates with the housing 9 using any known fastening technique to form a sealed cavitation chamber that includes the rotor head 19 and the external rotor 5.
  • the rotor head 19 is mounted to the housing cover 27 in any conventonal way to create the gap 25 as the second fluid heating zone between the external or outer surface 21 of the rotor head 19 and the inner surface 23 of the external rotor S.
  • openings 26 can be used with the appropriate fasteners.
  • the materials selected for the external rotor S and rotor head 19, and housing 9 and cover 27 are selected for optimal performance & safety.
  • Examples of materials for the housing 9 and cover 27 include polymers, e.g., a polyamide.
  • the external rotor 5 and rotor head 19 can be made from metal materials like aluminum or an alloy thereof or stainless steels.
  • the fluid to be heated or purified is introduced to the cavitation apparatus 10 through an intake port 29 located on the housing cover 27. While the position of the intake port 29 can vary, it is preferred to be positioned so that fluid entering the second fluid heating zone 25, see Figure 4, that is between the fixed internal rotor head 19 and the external rotor 5.
  • the cavitation zones 17 and 25 have special characterisics that allow for optimal cavitation to occur.
  • Figure 8 shows the location of these characterisitics.
  • Inner surface 15 of rotor housing 9, and inner surface 23 of external rotor 5 have directional bumpers 201 and 203, and bounce bumpers 202 and 204, respectively ,to channel the water on the direction path to ramp section 31 and 35 in each of these.
  • the directional bumpers 201 and 203 of these surfaces are longer, while the bouce bumpers 202 and 204 are shorter in length and allow the water to be channeled to the ramp zone 31 and 35, along the natural fluid direction Fd as depicted in the tetciary view Figure 7.
  • Each set of these bumpers is offset with the inner series to midrange series being offset 212, while the midrange series to outer series offset 213 to accomodate the variation of time for fluid molecule to travel in a cylindrical motion, and thus effect the cavitation zone velocity components Vx, Vv,and Vz in determing cavitation bore 33 and 37 locations.
  • This allows the internal rotor 21 and external rotor 5 to be consistent with standard manufacturing processes.
  • a perpendicular section 210 of directional bumbers 201 and 203 and bounce bumpers 202 and 204 to facilate a two dimesional discharge of fluids to the cavitation bores 33 and 37 is provided.
  • the cavitation bores 33 and 37 are located in the two dimensional plane, because the terciary velocity Vz has been driven to zero, such that distance between discharge zone 215 and cavitation bores 33, 37 is in direct correlation to speed of fluid F v .
  • the rotor head outer surface 21 is configured with a number of spaced apart cavitation bores 33 of a given depth and circumference.
  • the bores 33 cooperate with the wave ramp 31 and spiral shape of the inner surface 23 of the external rotor S to create a continuous and growing vacuum bubble generation in the regular arrangement of the cavitation bores 33 of the rotor head 19.
  • Heat is generated through the cavitation process of the fluid with virtually no destructive impact to the rotor head 19 or the cavitation bores 33.
  • the external rotor 5 is spinning in a clockwise direction, see Figure 4.
  • the fluid is compressed during the rotation cycle of the external rotor 5 and pressure increases in the fluid cavitation zone 25 and 17.
  • the entry to the wave ramps 31 and 35 provides an area of expansion that generates a rapid loss of pressure and this pressure reduction permites the forming of the cavitation bubbles and subsequent explosion in the cavitation bores 33 and 37.
  • the fluid After entering the zone 25, the fluid exits the zone 25 through multiple ports 34 at the rear face 36 of the external rotor 5. This exiting fluid then enters the other fluid cavitation zone 17 formed in the space between the inside surface 15 of the housing 1 and the outer surface 13 of the external rotor 5. In effect, the fluid is introduced to a secondary cavitation process, which is opposite in direction from a spinning fluid flow direction to the first cavitation process occuring in the zone 25 between the rotor head outer surface 21 and the inner surface 23 of the external rotor 5.
  • the housing 1 is equipped with the similar spiral configuration on the inner surface 15 thereof with a corresponding wave ramp 35 formed by the radial differences shown in Figure 3. That is, the radius Rl is less than radius R3 so as to form the wave ramp 35 in the tunnel zones 206 between directional bumpers 203 and bounce bumpers 204.
  • the external rotor 5 includes cavitation bores 37, like those in the rotor head ] 9.
  • Fluid exiting the first heating zone 25 is introduced into the second heating or cavitation zone 17.
  • the spinning fluid therein is then introduced into the regular arrangement of external rotor cavitation bores 37 in the same fashion as fluid is introduced into the bores 33 in the rotor head 19.
  • What is different between chambers 17 and 25 is the orientation of the wave ramps 31 and 35.
  • the wave ramp 35 is configured oppositely from the wave ramp 31
  • the spiral of increasing radius moves in the clockwise direction for surface 23 of the external rotor 5, short radius R2to longer radius R4.
  • the increasing radius moves in the counterclockwise direct, short radius Rl to longer radiusR3.
  • the faces of the wave ramps 31 and 35 are opposite to each other.
  • the wave ramp 35 has face 39, which is shown with a right angle configuration. However, the face 39 could be angled as well.
  • the spiral configuration insures the maximum vacuum bubble generation and the resulting heat generation bubble explosion.
  • the dual balanced cavitation process of the zone 17 and zone 25 occur simultaneously. Thus, through a single rotational cycle of the motor and external rotor 5, the fluid is processed twice forcavitation.
  • the primary wave ramps 31 and 35 be aligned at rest as shown in Figure 3. That is, the wave ramps 31 and 35 are at the 6 o'clock position.
  • the housing 1 Since the housing 1 is fixed and the apparatus would be positioned so that the axis A is horizontal, it is not a problem to have the wave ramp 35 in this position.
  • the wave ramp 31 of the external rotor 5 which can move due to its motor connection in this position, one way is to have the external rotor 5 balanced by the multiple outlet ports 34 such that the when motor 1 is not providing power, the external rotor 5 returns to the proper start up position in respect to the inner wave ramp 31 and the outer wave ramp 35. With this start up position, maximum heat generation of the fluid within the process is achieved. While the wave ramp position of the external rotor could vary from the 6 o'clock position, even as high as 90 degrees to either side, cavitation efficiency is lowered when varying from the preferable start up position.
  • the wave ramps 31 and 35 be at the 6 o'clock position as this facilitates the start up of the apparatus from a priming standpoint (the input 29 is aligned with the wave ramp 31 since the apparatus not only functions as a liquid cavitation device but also like a pump, drawing liquid in to the apparatus 10 and discharging it.
  • Varying from the 6 o'clock position towards either the 3 or the 9 o'clock reduces the pressure drop at the ramp and/or reduces the cavitation.
  • the cavitation device By changing this configuration of the cavitation zones 215 to alternative positions such as the 3 or 9 o'clock positions, in conjunction with varying the arc length LA, the cavitation device absorbed the heat of the fluid and produced a cooling effect, while maintaining the non-destructive nature of the caviation device.
  • the fluid being cavitated then leaves the cavitation apparatus 10 through an outlet port 41 in the cover 9 at low pressure ( ⁇ 1 atmosphere).
  • a total system should include the variable speed motor controller 301, a discharge water hammer tank 303, and an incoming storage tank 304 as a minimum.
  • the discharge water hammer tank 303 is set to 12-15 psi which insure proper noise control of heating water, while the incoming storage tank 304 allows for the cavitation apparatus 10 to operate at ambiant fluid flow. Because each fluid's physical properties vary with respect to temperature rise, as indicated in the chart of Figure 9 for water, it is important for the motor speed to be continually adjusted for speed control to insure cavitation process, specifically the distance for dishcarge zone 215 to cavitation bores 33, 37 is controlled.
  • control panel 302 will insure optimization of the cavitation process for the fluid under process by monitoring fluid temperature at probes 307 of intake and output of cavitation apparatus 10. Also, control valves 306 may be deployed with a crossover 308 to enhance system performance for certain applications such as purification.
  • the heated fluid can be used in any known application that employs a heated fluid
  • the invention is based on the realization that the objective of having a cavitation fluid heating apparatus without the known problems in prior art cavitation heating apparatus can be obtained by having a constricting form or interference in the zones or chambers 17 and 25 containing the wave ramp 35, directional bumpers 203, and bounce bumpers 204 between the rotating external rotor outer surface 13 and the inner surface 15 of the housing 9 and same constriction or interference as wave ramp 31 , directional bumpers 201 , and bounce bumpers 202 between the rotor head outer surface 21 and the external rotor inner surface 23.
  • the two chamber or zone design of Figures 1- 10 can be modified so that it is only a one chamber design and still function with all benefits with a single drive motor.
  • the rotor head 6 could be made without the cavitation bores and act only as a conduit to feed liquid to the zone 17 between the housing 1 and the external rotor 5.
  • the rotor head 6 could be eliminated so that only the external rotor 5 with its cavitation bores 37, the housing 9 with its specially configured inner surface 15, and the appropriate inlet and outlet ports would interact to heat the fluid.
  • This adaption of the invention allows for multiple size application configurations, with various motor sizes adaptable to a cavitation apparatus 10 for energy efficiency specific to the desired application.
  • the present invention is directed at releasing heat energy for use in delivering a fluid for heating, or cooling systems, fluid purification and separation, and any fluid processing that require heat to complete progression. Moreover, the invention, releases the energy through a cavitation process using less power consumption then traditional boiler systems or furnaces and significantly improves the energy and installation cost of purification system with similar capabilities.
  • the balanced internal fixed rotor 19, external rotor 5, wave ramps 31 and 35, directional bumpers 201 & 203, and bounce bumpers 202 & 204, and coinciding housing 1 and cover 27 provide the unique physical characteristics to produce heat at an increased rate of return of energy consumption while maintaining thermal characteristics.
  • the present invention comprises these unique component characteristics in a manner such that the fluid that the heat generated is retained for extended periods of time and thus requires lower cycles of energy consumption.
  • the present invention is unique such that the multistage cavitation process is initially completed through a primary cavitation rotor head that is stationary, with the external rotor acting as both a centrifugal source for the initial process and a cavitation element of the second stage. Both the external rotor and rotor housing have wave ramps to enhance the cavitation process. This allows the system to maximize the energy released from the cavitation process, while maintaining a low discharge pressure in so that energy is not lost by changing the state of the fluid to a gas.
  • the present invention configuration is such that the normally associated noise from the cavitation process is minimized and controlled.
  • the spiral configuration of the surfaces IS and 23 with the directional bumpers 201 and 203, and bounce bumpers 202 and 204 are an important feature of the invention.
  • This configuration allows for the creation and growth of the vacuum bubbles in the bores 33 and 37.
  • the vacuum bubbles are created among the molecules and surrounded by the fluid to be heated. The bubbles do not actually explode but crash, when they reach the cavitation bores 33 and 37.
  • the external rotor 5 is placed into the housing 1 and is rotated with the driving engine 1.
  • fluid to be heated is injected into the housing 1 through the input 29.
  • continuously growing vacuum bubbles are created among the liquid molecules in the bores 33 of the rotor head 6, if present, and in the bores 37 of the external rotor 5.
  • the vacuum bubble reaches the cavitation step 31 or 35, they crash.
  • the fluid to be heated is otherwise continuously flowed through the chambers 25 and 17, with the vacuum bubbles crashing in the expanding liquid after passing through the funnel zones 205.
  • the liquid molecules moving in opposite directions, explode. The heat generated during the explosion is absorbed by the surrounding liquid, and the heated liquid is ultimately extracted through the output 41.
  • one embodiment of the invention uses a single rotating cavitation body having bores in it, with the bores open to an outer surface of the cavitation body.
  • This cavitation body rotates within a housing and interacts with the cavitation step, which is located on the inside surface of the housing.
  • vacuum bubbles are created in the bores in the rotating body. The bubbles eventually grow such that they are no longer confined to the bores and crash into the cavitation step. This crash causes the liquid molecules to explode, which is the energy release that causes the heating of the water.
  • the cavitation step or wave form for the bores on the outer surface of the rotating body is on the inner surface of the housing.
  • the cavitation step for the bores on the outer surface of the stationary rotor head are on the inner surface of the rotating body.
  • the inventive system configuration allows the cavitation apparatus to produce heat energy at a significant increased ratio of energy utilization to consumption, while overcoming the traditional problems of prior systems; such as sonic sound waves (noise), bearing failures, and high discharge pressure energy losses.
  • the system consisting of control panel 302, variable speed motor controller 301, a discharge water hammer tank 303, incoming storage tank 304 and control valves 306 with crossover 308 enhance the capabilities of the cavitation apparatus 10.
  • the present invention through mechanic means, produces heated water at a 30-70% decreased rate of energy consumption (dependent upon the volume of fluid in the system) through a balanced cavitation furnace.
  • Another aspect of the invention is the ability of the apparatus to increase the density of the fluid being heated, e.g., water. Since it is known that less energy is needed to heat denser water, the increase in density of the water helps in increasing the efficiency of the fluid heating process.
  • Testing has been performed to monitor the heating effect of the inventive apparatus. This testing involved running the cavitation apparatus using different volumes of water to be heated and monitoring inlet water temperature, the volume of water flow rate, outlet water temperature of the cavitation apparatus, the temperature of the supply water to the apparatus, power of drive motor, electricity consumption, values of power, consumption of electricity power, and ambient temperature. This testing showed high efficiencies in terms of amount of heating done to the water as compared to the power used to run the apparatus.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Physical Or Chemical Processes And Apparatus (AREA)
  • Degasification And Air Bubble Elimination (AREA)
  • Food Preservation Except Freezing, Refrigeration, And Drying (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)

Abstract

La présente invention concerne un appareil à cavitation de fluide, comprenant un carter, un rotor externe dans une surface externe duquel se trouvent des trous de cavitation et un moteur permettant de faire tourner le rotor externe. La surface interne du carter est séparée de la surface externe du rotor externe par une distance, afin de créer une zone à cavitation de fluide. La surface interne du carter présente une forme en spirale et une zone tunnel pour améliorer les caractéristiques de transfert thermique du fluide pour le chauffage, le refroidissement et la purification. L'invention concerne également un système de commande pour faciliter la vitesse propre du moteur et le comportement du fluide afin d'améliorer le processus de cavitation.
PCT/US2018/013454 2017-01-13 2018-01-12 Procédé et appareil pour chauffer et purifier des liquides WO2018132640A1 (fr)

Priority Applications (12)

Application Number Priority Date Filing Date Title
CN201880011930.3A CN110637193B (zh) 2017-01-13 2018-01-12 加热和净化流体的方法和装置
JP2019558991A JP7152417B2 (ja) 2017-01-13 2018-01-12 液体を加熱及び浄化するための方法及び装置
RU2019125132A RU2752504C2 (ru) 2017-01-13 2018-01-12 Способ и устройство для нагрева и очистки жидкостей
KR1020197023653A KR102490810B1 (ko) 2017-01-13 2018-01-12 액체를 가열 및 정제하기 위한 방법 및 장치
EP18738867.3A EP3568649A4 (fr) 2017-01-13 2018-01-12 Procédé et appareil pour chauffer et purifier des liquides
SG11201906491QA SG11201906491QA (en) 2017-01-13 2018-01-12 Method and apparatus for heating and purifying liquids
MYPI2019003991A MY195794A (en) 2017-01-13 2018-01-12 Method and Apparatus for Heating and Purifying Liquids
MX2019008332A MX2019008332A (es) 2017-01-13 2018-01-12 Metodo y aparato para calentar y purificar liquidos.
CA3050252A CA3050252A1 (fr) 2017-01-13 2018-01-12 Procede et appareil pour chauffer et purifier des liquides
AU2018207118A AU2018207118B2 (en) 2017-01-13 2018-01-12 Method and apparatus for heating and purifying liquids
BR112019014380-7A BR112019014380B1 (pt) 2017-01-13 2018-01-12 Aparelho para aquecer um fluido, sistema de aparelho e método de alterar termicamente um fluido
IL267988A IL267988B2 (en) 2017-01-13 2019-07-11 Method and device for heating and purifying liquids

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US15/405,660 2017-01-13
US15/405,660 US20170130954A1 (en) 2014-03-11 2017-01-13 Method and apparatus for heating and purifying liquids

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WO2018132640A1 true WO2018132640A1 (fr) 2018-07-19

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WO2022144561A1 (fr) * 2020-12-28 2022-07-07 Sonolab Di Villa Pasquale Machine thermique à tourbillon d'eau en spirale
CN116446810A (zh) * 2023-06-16 2023-07-18 西南石油大学 一种间歇式振荡空化装置

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KR20230135288A (ko) * 2022-03-16 2023-09-25 장호섭 다중 유체역학적 캐비테이션 발생시스템 및 이를 이용한 유체 처리방법
CN117515933B (zh) * 2024-01-08 2024-03-08 河北环益新能源科技有限公司 一种动力水热设备

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US2683448A (en) 1951-07-12 1954-07-13 Leonard J Wolf Rotary mechanical heater
US3720372A (en) 1971-12-09 1973-03-13 Gen Motors Corp Means for rapidly heating interior of a motor vehicle
US4424797A (en) 1981-10-13 1984-01-10 Eugene Perkins Heating device
US4779575A (en) 1987-08-04 1988-10-25 Perkins Eugene W Liquid friction heating apparatus
US5385298A (en) 1991-04-08 1995-01-31 Hydro Dynamics, Inc. Apparatus for heating fluids
US5188090A (en) 1991-04-08 1993-02-23 Hydro Dynamics, Inc. Apparatus for heating fluids
US5279262A (en) * 1992-06-04 1994-01-18 Muehleck Norman J Mechanical liquid vaporizing waterbrake
US6227193B1 (en) 1995-04-18 2001-05-08 Advanced Molecular Technologies, L.L.C. Method for heating a liquid and a device for accomplishing the same
US6164274A (en) 1998-07-09 2000-12-26 Giebeler; James F. Apparatus and method for heating fluid
RU2262644C1 (ru) 2003-05-13 2005-10-20 Леонид Павлович Фоминский Нагреватель жидкости
US7658335B2 (en) * 2007-01-26 2010-02-09 Thermodynamic Process Control, Llc Hydronic heating system
US20100154772A1 (en) 2008-10-24 2010-06-24 Howard Harris Fluid Charged Rotary Heating System
WO2012164322A1 (fr) 2011-05-27 2012-12-06 Fabian Jozsef Équipement de cavitation pour produire des liquides chauffés, et sa méthode de fonctionnement
EP2918945A1 (fr) 2014-03-11 2015-09-16 US Intercorp LLC Procédé et appareil pour chauffer des liquides

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109028549A (zh) * 2018-09-06 2018-12-18 南通富莱克流体装备有限公司 热能泵
CN109028549B (zh) * 2018-09-06 2023-11-14 南通富莱克流体装备有限公司 热能泵
WO2022144561A1 (fr) * 2020-12-28 2022-07-07 Sonolab Di Villa Pasquale Machine thermique à tourbillon d'eau en spirale
CN116446810A (zh) * 2023-06-16 2023-07-18 西南石油大学 一种间歇式振荡空化装置
CN116446810B (zh) * 2023-06-16 2024-01-26 西南石油大学 一种间歇式振荡空化装置

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CA3050252A1 (fr) 2018-07-19
SG11201906491QA (en) 2019-08-27
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MX2019008332A (es) 2019-12-16
CN110637193A (zh) 2019-12-31
KR20190109443A (ko) 2019-09-25
CN110637193B (zh) 2021-11-23
RU2019125132A (ru) 2021-02-15
EP3568649A4 (fr) 2020-12-09
IL267988B2 (en) 2023-08-01
KR102490810B1 (ko) 2023-01-19
RU2019125132A3 (fr) 2021-05-24
EP3568649A1 (fr) 2019-11-20
SA519402029B1 (ar) 2022-09-20
RU2752504C2 (ru) 2021-07-28
BR112019014380B1 (pt) 2022-08-16
JP7152417B2 (ja) 2022-10-12

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