CN110637193A - Method and apparatus for heating and purifying fluids - Google Patents
Method and apparatus for heating and purifying fluids Download PDFInfo
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- CN110637193A CN110637193A CN201880011930.3A CN201880011930A CN110637193A CN 110637193 A CN110637193 A CN 110637193A CN 201880011930 A CN201880011930 A CN 201880011930A CN 110637193 A CN110637193 A CN 110637193A
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- fluid
- cavitation
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- housing
- rotor
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- 238000000746 purification Methods 0.000 abstract description 6
- 238000012546 transfer Methods 0.000 abstract description 4
- 238000001816 cooling Methods 0.000 abstract description 3
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Classifications
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- 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
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- 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
Abstract
A fluid cavitation device includes a housing, an outer rotor having cavitation holes on an outer surface thereof, and a motor for rotating the outer rotor. The inner surface of the housing is spaced apart from the outer surface of the outer rotor to form a fluid cavitation zone. The inner surface of the housing is provided with a spiral shape and channel regions to enhance the heat transfer characteristics of the fluid for heating, cooling and purification. A control system to facilitate appropriate motor speed and fluid behavior to enhance the cavitation process.
Description
Technical Field
The invention relates to a cavitation device for generating hot or cold fluid, comprising at least an engine, a housing, a fluid to be heated, and a sponge rotating in the fluid to be heated and driven by an external engine.
Background
Cavitation, which generates heat in a fluid such as water, is well known in the art.
Jacobs in U.S. patent No.3720372 presents an example of a cavitation system using a rotating body to produce a heated fluid. Other patented proposals for the generation of heat using cavitation have been developed in the 50's of the 20 th century, particularly in the united states. A notable patent is U.S. Pat. No.4424797 to Parkins, Inc. (Perkins). The development and prior art of the solution described in Smith, U.S. patent No.2683448, is the patent. An improvement is also disclosed in U.S. patent No.4779575 to parkis.
Cavitation devices are also described in U.S. Pat. Nos. 5188090 and 5385298 to Griggs. In these devices, a cylindrical body is placed in the housing of the device and the cover is provided with cavitation holes. Placing the fluid to be heated in the cylindrical free space between the rotating body with the cavity and the inner cover of the housing; as the cavitation body rotates, the pressure and temperature of the fluid increases. The Griggs patent is incorporated by reference herein in its entirety.
Other cavitation devices are disclosed in U.S. patent No.6164274 to gibeler, U.S. patent No.6227193 to Selivanov, and russian patent No. ru2262644. Another approach from the cavitation standpoint is disclosed in U.S. published patent application No.2010/0154772 to Harris. In this method, the helical ring of the rotating rotor and the inner cover of the housing together generate cavitation heat as the rotor rotates. A similar cavitation device is taught by Fabian patent WO2012/164322a 1.
The above-described prior art systems have a number of disadvantages including inefficiency and noise generation, primarily because these concepts consider the cavitation process as a two-dimensional process. It is an object of the invention to eliminate the disadvantages of the known solutions and the harmful cavitation effect in cavitation devices, to eliminate the destructive forces inside the cavitation process, to improve the efficiency and to reduce the cavitation noise by means of a three-dimensional vector method.
Disclosure of Invention
It is an object of the present invention to provide a cavitation device that produces sufficient heated fluid for fluid purification and other heat transfer methods, the cavitation device comprising at least one engine, a housing, a fluid to be heated, and one or more spongy cavitation bodies rotating in the fluid to be heated, driven by the engine. The invention includes a program for operation of the apparatus. The solution of the present invention advantageously eliminates other deleterious and erosive features of cavitation while using the cavitation bubbles produced to alter the thermal conditions of the fluid (primarily water) for water purification, HVAC applications, and other similar processes requiring heat transfer.
More specifically, the invention is characterized by the fact that the installation in the housing of a constriction comprising cavitation steps, directional and rebound bumpers, and a channel for free constriction of the fluid to be heated between the constriction and the cavitation body (2), allows a speed and direction control of the cavitation bubbles formed, which is crucial for the process integrity and for the reduction/elimination of the destructive forces associated with the cavitation process. The method of using the cavitation apparatus is also part of the present invention because the integral components of the entire cavitation system improve the noise reduction effect and treatment efficiency.
Brief description of the drawings
FIG. 1 shows a perspective view and an exploded view of one embodiment of the present invention.
Fig. 2 shows the top of the apparatus of fig. 1 with portions cut away to show detail.
Fig. 3 shows a cross-sectional view along the line III in fig. 2.
Fig. 4 shows an enlarged portion of the cross-sectional view of fig. 3.
Fig. 5 shows a more enlarged view of a portion of fig. 4.
FIG. 6 shows the discharge position, and cavitation hole position, in standard two-dimensional fashion, relative to motor speed and calculated fluid velocity at the discharge.
Figure 7 shows a typical cylindrical fluid path within the cavitation head in a third dimension.
Fig. 8 shows the general positions of the bumpers relative to each other to provide uniform discharge velocity of fluid to the cavitation aperture in the third dimension.
Figure 8A shows a cross-section at the inlet of the discharge channel in figure 8,
figure 8B shows a cross-section of figure 8 towards the discharge channel,
fig. 9 shows a water physical characteristic table, which changes with the temperature, requires speed control of the cavitation process,
fig. 10 illustrates the overall system requirements to produce a controlled three-dimensional cavitation process without negative destructive forces.
Detailed Description
Cavitation and its use in heating fluids is well known in the art.
Cavitation vacuum bubbles are generated in the low pressure portion of the fluid, primarily in the region of high velocity flow of the fluid. This phenomenon is common in the vicinity of central pumps, as well as marine propellers or turbines, and can widely erode the rotating propeller and all affected material surfaces.
This phenomenon is accompanied by vibrations and knocking-like noise; distorting the flow pattern, reducing the efficiency of the associated engine. Whatever the material the propeller or turbine blades are made of, cavitation can attack the respective surfaces, even the hardest alloys, and form tiny holes and cavities on the surfaces. The name for this phenomenon comes from this because cavitation means the creation of a cavity. For the reasons mentioned above, cavitation is generally a phenomenon that needs to be eliminated.
Cavitation vacuum bubbles are typically small, only a few millimeters in size, and are generated by a sudden drop in pressure in a high velocity fluid stream between fluid molecules. If the pressure of the high pressure fluid suddenly drops, the bubbles collide as they enter the high pressure region, or collapse and uniformly fill the space with droplets. A small cavity is created between the droplet and the droplet molecules, creating a true vacuum bubble. This collision of the vacuum bubbles is then accompanied by low collision noise and light emission. The impact of a large number of fluid molecules can create cracks, bounces, and rumble. When the bubbles collide, the energy stored in the bubbles, i.e., a large amount of heat and light energy, is released. Energy diffuses at different frequencies and is absorbed by adjacent molecules, thereby increasing their temperature. In other words, the generated gas reaches a state higher than the temperature and pressure of the saturated gas, the molecular adhesion is broken, and the bubble is abruptly broken. The high temperatures thus generated are absorbed by the surrounding fluid molecules, thereby heating the fluid. The heat generated during cavitation is sufficient to eliminate any bacteria, viruses, heavy metals, and other contaminants in the fluid, providing additional purification benefits. In fact, the purified fluid is most suitable for controlling the three-dimensional cavitation process.
Also, it has been known for many years to utilize this phenomenon to heat fluids. However, the generation of cavitation to heat a fluid has been indirect, e.g., using a rotating body driven by an electric motor, more expensive than directly using an electrically heated fluid. On the other hand, the situation is different if other economic power sources are available, such as turbines, gasoline or diesel engines, etc. Using such a power supply, purified heated fluid can be directly produced.
As noted above, in the system shown in the Griggs patent, the fluid is circulated at a selected high velocity in a closed system and flows through a narrowing channel, where the fluid is abruptly introduced into an expansion section (cavitation orifice) and must be depressurized to produce cavitation.
Cavitation is generally a detrimental phenomenon because it is destructive, produces a large amount of heat energy, high discharge pressure and noise. The present invention is, however, based on the recognition that an improved cavitation device can be manufactured by installing a constriction or interference configuration between the rotating cavitation body and the inner surface of the housing containing the cavitation body, optionally between the rotating cavitation body and the inner surface of the secondary stationary rotor head. In this case, the vacuum bubble is ensured to continuously explode. By designing the interior of the housing with interference or shrinkage, the fluid to be heated surrounds the vacuum bubbles in the holes upon detonation, cavitation noise can be reduced, and the detrimental effects of cavitation can be reduced or eliminated.
In one aspect, the invention provides a cavitation device for producing heated purified fluid comprising at least a motor, a housing, a fluid to be heated, and a rotating cavitation body driven by the motor to rotate in the fluid to be heated. The engine may be an electric engine, but a steam or internal combustion engine, or the rotating shaft of a turbine, may also be used to drive the cavitation device. A stationary rotor head may be placed inside the rotating cavitation body forming a second fluid heating zone. The invention also includes methods of operation of the apparatus requiring extensive supply of fluid, such as water, to the apparatus for cavitation purposes, followed by heating of the fluid as is known in the art. While water is a desirable fluid, the device can be used to heat and purify any fluid if desired.
The advantages of the present invention are amplified by having cavitation holes in the rotating cavitation body and rotor head (if present). Like the Griggs patents, the external surface of the rotating cavitating body is provided with cavitating pores. The cavitation orifice and the cavity between the rotating cavitation body and the surrounding housing form a cavitation flow zone. In the embodiment using a stationary rotor head, the outer surface of the rotor head is also equipped with cavitation holes so as to face the inner surface of the rotating cavitation body, which is generally annular. This creates an additional fluid cavitation flow zone between the interior of the rotating cavitation body and the rotor head to enhance cavitation of the fluid.
Fig. 1-10 illustrate one embodiment of the present invention. The device is designated by reference numeral 10 and comprises an external motor 1 for rotating a rotating cavitating body or external rotor 5 via a direct drive shaft 3, which drive shaft 3 comprises a shaft seal 7. Drive shaft 3 extends through opening 6 of end 8 of housing 9 and opening 12 of outer rotor 5. The outer rotor 5 may rotate at any speed depending on the viscosity of the heated fluid. Typically at 2500-. However, to improve the Griggs patent and precisely locate the cavitation bubbles exiting to the cavitation apertures 33, 37 in the third dimension, the motor speed is tuned to the device 10 using the variable speed control 301 and the directional and rebound bumpers. This produces a precise shaft speed SvIs of importance, which determines the horizontal velocity V of the fluid at the discharge zones 31, 35 of the device 10XVertical velocity VYAnd third dimension velocity VZ. The fluid is dischargedThe hopper is compressed, guided and at a specific speed FVRelease at the specific speed FVBy the length L of the physical arc between cavitation zones (FIG. 6)AThe actual number of cavitation discharge zones with a given cavitation head at any particular motor speed is determined. Due to the velocity F of the fluidvCan be adjusted so that it can be determined that the fluid molecules follow the path LAThe time taken to travel and the horizontal and vertical components of the fluid at the discharge zones 31, 35 can be calculated. The measured function of the horizontal velocity of the curvilinear motion is Vx＝dx/dtAnd the vertical velocity is Vy＝dyDt, third dimension velocity VZ＝dZ/dt. The purpose of designing the directional and rebound bumpers is to reduce the third dimension velocity VzDrive to zero by eliminating dZComponent, thereby solving for dxAnd dyThe location of cavitation orifices 33, 37, and orifice B, may be determined relative to the time of tuning (i.e., motor speed)AThe distance between them. Fig. 6 shows only two cavitation holes, but it should be understood that the cavitation holes extend along the circumference of the outer rotor as shown in fig. 3.
A rotor housing 9 is provided which has no internal bearings. The presence of the inner bearing is a critical failure mode of the Fabian patent because in this design the bearing will be directly affected by the heat transfer of the fluid to the bearing during cavitation. Accordingly, the shaft 3 of the motor 1 extends through the housing 9 and supports the outer rotor 5 to rotate in a cantilever structure. When the shaft 3 extends through the housing 9, the shaft 3 of the motor is longer than the normal and inner bearings in the motor to support the balanced outer rotor 5. Housing 9 forms a cavity 11 to receive outer rotor 5. A conventional shaft seal (not shown) is located between the motor shaft 3 and the housing 9 for sealing. By the cantilevered arrangement of the motor shaft and the association of the bearings with the motor for shaft support, the problem of bearing failure in prior art devices is eliminated.
In operation, during operation of the apparatus 10, fluid (e.g., water) is introduced into the chamber 11 at a rate that depends on the optimal tuning speed of the motor to the fluid. When outer rotor 5 is positioned within the housing, outer surface 13 of outer rotor 5 faces inner surface 15 of housing 9. There is a gap 17 between the two surfaces 13 and 15, the gap 17 being a fluid heating zone of the apparatus 10, including three lateral cavitation zones 215.
In the embodiment of fig. 1-10, there are three sets of three discharge zones 31 and 35 for heating zone 17, and the same arrangement for heating zone 25, so there are six fluid heating zones, and thus 18 cavitation zones 215 in total. The number of cavitation zones can be increased or decreased by changing the size of the cavitation head to obtain an additional arc length L consistent with a selected motor speedA. This is achieved by providing a secondary rotor head 19 with a specific rotational pitch or configuration and having similar physical properties as outer rotor 5 to enhance the energy in the fluid. The outer surface 21 of the rotor head 19 faces the inner surface 23 of the outer rotor 5 with a gap therebetween. This gap forms another fluid heating zone 25 of the device 10.
A housing cover 27 is also provided. Housing cover 27 is mated with housing 9 using any known fastening technique to form a sealed cavitation chamber that includes rotor head 19 and outer rotor 5. Rotor head 19 is mounted to housing cover 27 in any conventional manner to create gap 25 as a second fluid heating zone between outer surface 21 of rotor head 19 and inner surface 23 of outer rotor 5. As an example of installation, the openings 26 may be used with suitable fasteners.
The materials of outer rotor 5 and rotor head 19, as well as housing 9 and cover 27, are chosen so as to obtain optimum performance and safety. Examples of materials for the housing 9 and the cover 27 include polymers, such as polyamide. The outer rotor 5 and the rotor head 19 may be made of a metallic material such as aluminum or an alloy thereof or stainless steel.
The fluid to be heated or purified is introduced into the cavitation device 10 via an introduction port 29 located on the housing cover 27. Although the location of the intake 29 can vary, it is preferably located between the fixed inner rotor head 19 and the outer rotor 5, see fig. 4, so as to allow fluid to enter the second fluid heating zone 25.
Cavitation zones 17 and 25 have special features to optimize cavitation. The location of these features is shown in fig. 8. The inner surface 15 of the rotor housing 9 and the inner surface 23 of the outer rotor 5 have a respective oneThere are directional bumpers 201 and 203, and bounce bumpers 202 and 204 to direct water along a directional path to the ramps 31 and 35 in each of these bumpers. The directional bumpers 201 and 203 on these surfaces are longer, while the rebound bumpers 202 and 204 are shorter in length, allowing water to follow the natural fluid direction FdLeading to the ramp regions 31 and 35 as shown in the third dimensional view of fig. 7. Each of these buffers has an inner and middle offset 212 and an outer and middle offset 213 to accommodate the variation in time of the fluid molecules along the cylinder motion, thereby affecting the cavitation zone velocity component VX、VYAnd VZTo determine the location of cavitation holes 33 and 37. This makes the inner rotor 21 and the outer rotor 5 conform to standard manufacturing processes.
In addition, the fluid path that allows for evacuation is three-dimensional, where locating and forming cavitation holes 33 and 37 presents geometric manufacturing issues, the vertical portion 210 of directional dampers 201 and 203, and rebound dampers 202 and 204 are provided to facilitate two-dimensional evacuation of fluid to cavitation holes 33 and 37. Cavitation holes 33 and 37 lie in a two-dimensional plane due to the third dimension velocity VZHas been driven to zero such that the distance between discharge zone 215 and cavitation holes 33, 37 and fluid velocity FvAre directly related. By precisely positioning the discharge fluid in alignment with cavitation holes 33 and 37, uncontrolled release of destructive cavitation bubbles in areas without cavitation holes is prevented. This is achieved by the shape of inner surface 23 of outer rotor 5 in funnel region 205 between directional damper 201 and rebound damper 202. The ramp surface has a helical shape, which is represented by the radial distance as measured from the central axis and longitudinal axis a of the device 10. Referring to fig. 3, one radius R2 measured from the central axial point of the device is smaller than the other radius R4. This difference in the radius and the helical shape of the inner surface 23 of the outer rotor 5 creates a wave slope 31. The pressure differential created by this configuration is critical to the formation of cavitation vacuum bubbles at the wave ramp 31.
The rotor head outer surface 21 is configured with a plurality of spaced cavitation holes 33 of a given depth and circumference. Holes 33 cooperate with wave ramps 31 and the helical shape of inner surface 23 of outer rotor 5 to produce a continuous and growing vacuum bubble under the regular arrangement of cavitation holes 33 of rotor head 19. The heat is generated by the cavitation process of the fluid with little destructive effect on the rotor head 19 or the cavitation orifice 33. In operation, outer rotor 5 rotates in a clockwise direction as shown in fig. 4. The fluid is compressed during the rotational cycle of the outer rotor 5 and the pressure in the fluid cavitation zones 25 and 17 increases. Entering the wave ramps 31 and 35 provides an expansion zone that produces rapid pressure loss and this pressure drop forms cavitation bubbles that subsequently explode in the cavitation holes 33 and 37.
After entering region 25, the fluid exits region 25 via a plurality of ports 34 at a rear surface 36 of outer rotor 5. The outflowing fluid then enters another fluid cavitation zone 17 formed in the space between inner surface 15 of housing 1 and outer surface 13 of outer rotor 5. In effect, the fluid is introduced into a second cavitation process in a direction opposite to the direction of flow of the spin fluid from which the fluid is introduced into the first cavitation process, which occurs in region 25 between rotor head outer surface 21 and inner surface 23 of outer rotor 5.
The inner surface 15 of the housing 1 has a similar helical configuration with corresponding undulating ramps 35 formed by the radial differences shown in figure 3. That is, the radius R1 is smaller than the radius R3 so as to form the wave-shaped ramp 35 in the passage area 206 between the directional buffer 203 and the rebound buffer 204.
Outer rotor 5 includes cavitation holes 37, similar to those in rotor head 19.
The fluid leaving the first heating zone 25 is directed into the second heating or cavitation zone 17. The rotating fluid therein is then introduced into the regular arrangement of outer rotor cavitation holes 37 in the same manner as the fluid is introduced into holes 33 in rotor head 19. The difference between chambers 17 and 25 is the direction of the wave ramps 31 and 35. The waveform ramp 35 is disposed opposite the waveform ramp 31.
In other words, referring to fig. 3, the increased radius spiral moves in a clockwise direction relative to surface 23 of outer rotor 5, from a short radius R2 to a longer radius R4. The increasing radius moves directly in a counterclockwise direction, relative to the surface 15 of the housing 9, from a short radius R1 to a longer radius R3. This means that the faces of the wave-shaped inclined surfaces 31 and 35 are opposed to each other. Referring to fig. 5, the wave ramp 35 has a face 39, which is shown in a right angle configuration. However, the face 39 may also be angled. The spiral configuration ensures that a maximum vacuum bubble is generated, and the heat generated thereby causes the bubble to explode. The dual equilibrium cavitation process of region 17 and region 25 occurs simultaneously. Thus, the fluid is subjected to the cavitation process twice via a single rotation cycle of the motor and the outer rotor 5.
As shown in fig. 3, it is also desirable for the hole heating process that the major wave ramps 31 and 35 be aligned at rest. That is, both wave ramps 31 and 35 are at the 6 o' clock position.
Since the housing 1 is fixed and the position of the device is set so that the axis a is horizontal, it is not a problem to provide the wave ramp 35 at this position. In order to enable the wave ramps 31 of the outer rotor 5 to move in this position due to its motor connection, one way is to balance the outer rotor 5 via a plurality of outlets 34 so that when the motor 1 is not providing power, the outer rotor 5 returns to the appropriate starting position relative to the inner wave ramps 31 and the outer wave ramps 35. In this activated position, the heat generated by the fluid during the process is maximized. While the wave ramp position of the outer rotor can vary from the 6 o' clock position even up to 90 degrees to either side, cavitation efficiency decreases when varying from the preferred start position. It is also preferred that the wave ramps 31 and 35 are at the 6 o' clock position because this facilitates activation of the device from an activation angle, with the inlet 29 aligned with the wave ramp 31, because the device functions not only as a fluid cavitation device, but also as a pump, drawing fluid into the device 10 and expelling it. Changing from the 6 o ' clock position to the 3 o ' clock or 9 o ' clock position may reduce the pressure drop at the ramp and/or reduce cavitation. By changing the configuration of the cavitation zone 215 to an alternate position, such as the 3 o 'clock or 9 o' clock position, while changing the arc length LAThe cavitation device absorbs heat from the fluid and produces a cooling effect while maintaining the non-destructive nature of the cavitation device.
The cavitated fluid then exits the cavitation device 10 at low pressure (<1 atmosphere) via an outlet 41 in the cover 9. To achieve maximum efficiency and eliminate the destructive elements of cavitation, the overall system should include at least a variable speed motor controller 301, a discharge water hammer tank 303, and an incoming storage tank 304. The discharge ram box 303 is set at 12-15psi, which ensures proper control of the noise of the heated water, while the incoming storage tank 304 allows the cavitation device 10 to operate at ambient fluid flow. Because the physical properties of each fluid vary with increasing temperature, as shown in fig. 9, where the fluid is water, it is important to continuously adjust the motor speed for speed control to ensure the cavitation process, and in particular to control the distance 215 of the discharge zone to the cavitation orifice 33, 37. By adjusting the motor speed in accordance with the physical characteristics of the fluid at any given temperature or other variable, it can be ensured that the distance from the funnel region 205 to the cavitation apertures 33, 37 remains non-destructive. The additional control panel 302 will ensure optimization of the cavitation process for the fluid being treated by monitoring the fluid temperature at the probes 307 at the inlet and outlet of the cavitation device 10. In addition, control valve 306 may be configured with crossover line 308 to enhance system performance in certain applications, such as purging. The heated fluid may be used in any known application where a heated fluid is used.
The present invention achieves the object of providing a cavitation fluid heating device which does not have the problems known in the prior art, the device of the invention being obtained by: having a constricting configuration or interference in regions or chambers 17 and 25, including wave ramps 35, directional bumpers 203 and rebound bumpers 204 between rotating outer rotor outer surface 13 and inner surface 15 of housing 9, and the same constricting configuration or interference between rotor head outer surface 21 and outer rotor inner surface 23, such as wave ramps 31, directional bumpers 201, and rebound bumpers 202. By designing the inner surface 15 of the housing 1 and the inner surface 23 of the outer rotor 5 in this way, vacuum bubble explosion can be continuously ensured. By designing the helicoids 15 and 23, directional dampers 201 and 203, and rebound dampers 202 and 204 to surround the vacuum bubbles in the bore when the fluid to be heated explodes, cavitation noise is reduced and other deleterious effects of cavitation, such as corrosion of components, are reduced or eliminated.
In a significant change to the design of the Fabian, it should be understood that the two chamber or zone design of fig. 1-10 can be modified such that it is only one chamber design and still have all the benefits of a single drive motor. It is thus possible to manufacture the rotor head 6 without cavitation holes and to use it only as a conduit, supplying fluid to the region 17 between the casing 1 and the outer rotor 5. In yet another embodiment, rotor head 6 can be eliminated, so that there is only an outer rotor 5 with cavitation holes 37, a housing 9 with a specially configured inner surface 15, and appropriate inlets and outlets that will interact to heat the fluid. This improvement of the present invention allows for a variety of size application configurations, with different motor sizes being suitable for the cavitation device 10 to achieve energy efficiencies specific to the desired application.
While the single chamber device provides heated fluid without many of the cavitation-related problems of the prior art devices, it is advantageous to employ the embodiment of fig. 1-10, wherein the outer rotor is fitted with a fixed rotor head 19, the outer surface being provided with additional cavitation holes 33. This structure, together with the associated system components, enables the gerotor to generate thermal energy at a significantly improved energy utilization to consumption ratio while overcoming the conventional problems of prior systems such as acoustic waves (noise), bearing failure, and high discharge pressure energy losses.
The present invention relates to the release of thermal energy for fluid transport, fluid purification and separation in heating or cooling systems, and any fluid treatment that requires heating to complete progress. Furthermore, the present invention releases energy through the cavitation process, which is lower than the power consumption of conventional boiler systems or furnaces, significantly improving the energy and installation costs of purification systems with similar capabilities. The balanced internal stationary rotor 19, outer rotor 5, wave ramps 31 and 35, directional dampers 201 and 203, rebound dampers 202 and 204, and coincident housing 1 and cover 27 provide unique physical characteristics to generate heat at an increased rate, returning energy consumption while maintaining thermal characteristics.
The present invention includes these unique component characteristics such that the fluid of generated heat is retained for long periods of time, thus requiring lower energy consumption cycle times.
The unique feature of the present invention is that the multistage cavitation process is initially completed by a stationary main cavitation rotor head, with the outer rotor acting both as the centrifugal source for the initial process and as the cavitation element for the second stage. Both the outer rotor and the rotor housing have wave ramps to enhance the cavitation process. This maximizes the energy released by the system from the cavitation process while maintaining a low discharge pressure so that no energy is lost by changing the fluid state to a gas. The structure of the present invention allows the normally associated noise from the cavitation process to be minimized and controlled.
As mentioned above, the spiral configuration of surfaces 15 and 23 with directional bumpers 201 and 203 and rebound bumpers 202 and 204 is an important feature of the present invention. This configuration allows the creation and growth of vacuum bubbles in the holes 33 and 37. In the holes 33 and 37, vacuum bubbles are generated between the molecules and are surrounded by the fluid to be heated. When the bubbles reach the cavitation holes 33 and 37, the bubbles do not actually explode but collide.
According to this method, the outer rotor 5 is placed in the housing 1 and rotates together with the drive motor 1. During rotation, the fluid to be heated is injected into the housing 1 via the inlet 29. By means of the rotation, growing vacuum bubbles are created between the fluid molecules in the holes 33 of the rotor head 6 (if present) and the holes 37 of the outer rotor 5. Once the vacuum bubbles reach the cavitation step 31 or 35, they collide. The fluid to be heated otherwise flows continuously through chambers 25 and 17, the vacuum bubbles colliding in the expanding fluid after passing through funnel region 205. Upon collision, fluid molecules moving in the opposite direction explode. The heat generated during the explosion is absorbed by the surrounding fluid, which is eventually extracted via the outlet 41.
An advantage of the cavitation device according to the present invention is that the detrimental effects of cavitation are successfully eliminated or reduced using flow channels designed for the fluid to be heated and the procedure of operation of the apparatus.
Returning to the embodiments discussed above, one embodiment of the present invention uses a single rotating cavitation body with an aperture that opens to the outer surface of the cavitation body. The cavitation body rotates within the housing and interacts with a cavitation step located on an inner surface of the housing. During the rotation, vacuum bubbles are generated in the holes of the rotating body. The bubbles eventually grow so that they are no longer confined within the holes and hit the cavitation steps. This collision causes the fluid molecules to explode, which is the release of energy, causing the water to be heated.
In another embodiment, there are two sets of holes, one set located on the outer surface of the rotating body and the other set located on the outer surface of the second stationary part inside the rotating body. In this dual orifice embodiment, the cavitation step or wave shape for the orifice on the outer surface of the rotating body is located on the inner surface of the housing. A cavitation step for fixing the hole on the outer surface of the rotor head is located on the inner surface of the rotating body.
The system configuration of the present invention allows the cavitation device to generate thermal energy at a significantly increased energy utilization to consumption ratio while overcoming the conventional problems of prior systems such as acoustic waves (noise), bearing failure and high discharge pressure energy losses. The system consisting of the control panel 302, variable speed motor controller 301, discharge water hammer tank 303, intake reservoir 304 and control valve 306 with crossover 308 enhances the capacity of the cavitation device 10.
The present invention employs mechanical means to produce hot water at a reduced energy consumption rate (depending on the volume of fluid in the system) of 30-70% via a balanced evacuation furnace to reduce energy consumption.
Another aspect of the invention is the ability of the device to increase the density of the fluid (e.g., water) being heated. It is well known that less energy is required to heat the more dense water, and therefore the increase in density of the water helps to increase the efficiency of the fluid heating process.
Tests have been conducted to monitor the heating effect of the device of the present invention. The test includes operating the cavitation device with different volumes of water to be heated and monitoring the inlet water temperature, the water flow volume, the outlet water temperature of the cavitation device, the temperature of the water supplied to the device, the drive motor power, the power consumption, the power value, the power consumption, and the ambient temperature. This test shows that the efficiency of the water heating is high compared to the power used to operate the device.
Accordingly, the present invention has been made in accordance with the preferred embodiments thereof, which fulfills each and every one of the objects of the present invention as set forth above and provides a new and improved fluid heating apparatus using cavitation.
Of course, various changes, modifications and alterations from the teachings of the present invention may be contemplated by those skilled in the art without departing from the intended spirit and scope of the present invention. The invention is limited only by the terms of the appended claims.
Claims (14)
1. An apparatus for heating a fluid using cavitation, comprising:
a housing having an inlet for fluid to be heated and an outlet for discharging heated fluid from the housing;
an outer rotor adapted to be fixed to a motor shaft and received within the housing and further adapted to rotate within the housing, the outer rotor having a plurality of cavitation holes disposed on an outer surface thereof and being disposed within the housing, a fluid heating zone being formed between an outer surface of the outer rotor and an inner surface of the housing facing the outer surface of the outer rotor,
wherein the inner surface of the housing facing the outer surface of the outer rotor containing the bore has a plurality of laterally spaced first channel regions extending circumferentially along the inner surface, each of the first channel regions terminating in a first discharge region, each of the first channel regions including a first ramp, each of the first discharge regions being offset from an adjacent first discharge region, fluid entering the housing being heated by interaction with the first channel regions and first ramps, the bore in the outer rotor, and the rotation of the outer rotor.
2. The apparatus of claim 1, further comprising a stationary rotor head mounted within the housing, and an outer surface thereof facing an inner surface of the outer rotor, the outer surface of the fixed rotor head and the inner surface of the outer rotor forming a second fluid cavitation zone, said outer surface of said fixed rotor head including a plurality of cavitation holes therein, said inner surface of said outer rotor having a plurality of laterally spaced apart second channel regions, the second channel regions extend circumferentially along the inner surface of the outer rotor, each of the second channel regions terminating in a second discharge region, each of the second channel regions including a second ramp, each of the second discharge regions being offset from an adjacent second discharge region, fluid entering the second fluid cavitation region being heated by interaction with the second channel regions and second ramps, the apertures in the rotor head, and the rotation of the outer rotor.
3. The apparatus of claim 1, wherein the cavitation device has a horizontal longitudinal axis, each of the first discharge zones being located at a 6 o ' clock position to heat the fluid and at a 3 o ' clock position or a 9 o ' clock position to cool the fluid when viewed in a cross-section transverse to the horizontal longitudinal axis.
4. The apparatus of claim 2, wherein the cavitation device has a horizontal longitudinal axis and each of the first and second discharge zones is located at a 6 o ' clock position to heat the fluid and at a 3 o ' clock position or a 9 o ' clock position to cool the fluid when viewed in a cross-section transverse to the horizontal longitudinal axis.
5. The device of claim 1, wherein the first channel region has a face at the first discharge region on the inner surface of the housing that forms a right angle with respect to the inner surface.
6. The apparatus of claim 2, wherein each of the first channel zones has a face at each of the first discharge zones on the inner surface of the housing that forms a right angle with respect to the inner surface of the housing, and each of the second channel zones has a face at each of the second discharge zones on the inner surface of the outer rotor that forms a substantially right angle with respect to the inner surface of the outer rotor.
7. A cavitation device system, comprising:
a) the apparatus of claim 1;
b) a water inlet tank communicated with the inlet of the housing,
c) a drain hammer case in communication with the outlet of the housing,
d) a motor having a motor shaft on which the outer rotor is mounted,
e) a motor controller for controlling a speed of the motor,
f) a thermometer for monitoring fluid in and out of the device; and
g) a crossover tube between the inlet of the inlet tank and the outlet of the drain hammer case.
8. The system of claim 7, wherein the outer rotor is mounted to the motor shaft in a cantilever configuration such that there are no internal bearings in the device.
9. A method of utilizing cavitated heat exchange fluid comprising the steps of:
a) providing the apparatus of claim 1;
b) introducing a fluid into the inlet;
c) rotating the outer rotor at a controlled speed to heat the fluid to improve alignment of bubbles with cavitation holes, and
d) discharging the heat-exchanged fluid from the outlet.
10. The method of claim 6, wherein the fluid is water.
11. A method of utilizing cavitated heat exchange fluid comprising the steps of:
a) providing the apparatus of claim 2;
b) introducing a fluid into the inlet;
c) rotating the outer rotor at a controlled speed to heat the fluid to improve alignment of the bubbles with the cavitation holes;
d) discharging the heat-exchanged fluid from the outlet; and
e) the control system described in claim 7.
12. The method of claim 11, wherein the fluid is water.
13. The method of claim 9, wherein the fluid is purified.
14. The method of claim 11, wherein the fluid is purified.
Applications Claiming Priority (3)
| 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 |
| PCT/US2018/013454 WO2018132640A1 (en) | 2017-01-13 | 2018-01-12 | Method and apparatus for heating and purifying liquids |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN110637193A true CN110637193A (en) | 2019-12-31 |
| CN110637193B CN110637193B (en) | 2021-11-23 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201880011930.3A Active CN110637193B (en) | 2017-01-13 | 2018-01-12 | Method and apparatus for heating and purifying fluids |
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| Country | Link |
|---|---|
| EP (1) | EP3568649A4 (en) |
| JP (1) | JP7152417B2 (en) |
| KR (1) | KR102490810B1 (en) |
| CN (1) | CN110637193B (en) |
| AU (1) | AU2018207118B2 (en) |
| BR (1) | BR112019014380B1 (en) |
| CA (1) | CA3050252A1 (en) |
| IL (1) | IL267988B2 (en) |
| MX (1) | MX2019008332A (en) |
| MY (1) | MY195794A (en) |
| RU (1) | RU2752504C2 (en) |
| SA (1) | SA519402029B1 (en) |
| SG (1) | SG11201906491QA (en) |
| WO (1) | WO2018132640A1 (en) |
Cited By (1)
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| CN117515933A (en) * | 2024-01-08 | 2024-02-06 | 河北环益新能源科技有限公司 | Power hydrothermal equipment |
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| CN109028549B (en) * | 2018-09-06 | 2023-11-14 | 南通富莱克流体装备有限公司 | heat energy pump |
| WO2022144561A1 (en) * | 2020-12-28 | 2022-07-07 | Sonolab Di Villa Pasquale | Thermal machine with spiral water vortex |
| KR20230135288A (en) * | 2022-03-16 | 2023-09-25 | 장호섭 | Multiple hydrodynamic cavitation generation system and fluid treatment method using the same |
| CN116446810B (en) * | 2023-06-16 | 2024-01-26 | 西南石油大学 | Intermittent type formula oscillation cavitation device |
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Also Published As
| Publication number | Publication date |
|---|---|
| CA3050252A1 (en) | 2018-07-19 |
| CN110637193B (en) | 2021-11-23 |
| AU2018207118B2 (en) | 2023-11-09 |
| WO2018132640A1 (en) | 2018-07-19 |
| BR112019014380B1 (en) | 2022-08-16 |
| IL267988A (en) | 2019-09-26 |
| AU2018207118A1 (en) | 2019-08-29 |
| KR20190109443A (en) | 2019-09-25 |
| EP3568649A1 (en) | 2019-11-20 |
| IL267988B2 (en) | 2023-08-01 |
| JP2020514671A (en) | 2020-05-21 |
| MY195794A (en) | 2023-02-21 |
| SG11201906491QA (en) | 2019-08-27 |
| BR112019014380A2 (en) | 2020-02-11 |
| JP7152417B2 (en) | 2022-10-12 |
| RU2019125132A (en) | 2021-02-15 |
| KR102490810B1 (en) | 2023-01-19 |
| MX2019008332A (en) | 2019-12-16 |
| SA519402029B1 (en) | 2022-09-20 |
| RU2019125132A3 (en) | 2021-05-24 |
| RU2752504C2 (en) | 2021-07-28 |
| EP3568649A4 (en) | 2020-12-09 |
| IL267988B1 (en) | 2023-04-01 |
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