VORTEX CAVITATOR
The tandem configuration of vortex cavitators addresses inefficiencies in existing designs by reducing hydraulic and hydrodynamic losses, achieving lower energy consumption and increased efficiency with flexible operation.
Patent Information
- Authority / Receiving Office
- RU · RU
- Patent Type
- Utility models
- Current Assignee / Owner
- FEDERALNOE GOSUDARSTVENNOE BYUDZHETNOE OBRAZOVATELNOE UCHREZHDENIE VYSSHEGO OBRAZOVANIYA NIZHEGORODSKIJ GOSUDARSTVENNYJ AGROTEKHNOLOGICHESKIJ UNIVERSITET IMENI L YA FLORENTEVA (FGBOU VO NIZHEGORODSKIJ GATU IM L YA FLORENTEVA)
- Filing Date
- 2026-03-02
- Publication Date
- 2026-06-30
AI Technical Summary
Existing vortex cavitators suffer from significant hydrodynamic and hydraulic losses due to fluid rotation, friction, and inefficient return line designs, leading to high energy consumption and reduced efficiency.
A paired structure of vortex cavitators is introduced, where each cavitator is connected in tandem, eliminating the need for a return pipeline and incorporating an additional vortex cavitator to reduce power consumption and hydraulic losses, while maintaining efficiency through pre-swirling fluid flow alignment with the impeller blades.
This configuration significantly reduces energy consumption, increases efficiency, and enhances flexibility by allowing for single or dual operation based on heating requirements, achieving lower power consumption and higher thermal output with reduced operational costs.
Smart Images
Figure 00000001_ABST
Abstract
Description
[0001] The utility model relates to cavitation-type heat generators for heating liquids in hydraulic systems for various purposes, and can also be used as mixers of various liquids, dispersion, destruction of molecular bonds in complex liquids, changing the physical and mechanical properties of liquids, for influencing biological objects.
[0002] A vortex heater - heat generator is known according to the patent of the Russian Federation No. 2045715, class F 25 B 29 / 00, 1995, containing a cylindrical body, a liquid movement accelerator made in the form of a cyclone, the end side of which is connected to the body, at the outlet of which a braking device is located, connected to the outlet pipe.
[0003] A distinctive feature of this design is the cyclone, which is constructed in the form of a snail. When the incoming flow and the flow that has completed almost a full revolution merge, an acoustic signal is generated due to the competition between them (Fig. 1). The resulting sound wave propagates into the housing and is amplified within it due to its transformation into a standing wave. This causes a rupture of the liquid continuity and the formation of cavitation cavities in the vacuum phase, and the collapse of these cavities with the release of thermal energy in the manometric phase (Fig. 2).
[0004] However, this device has a number of drawbacks: it suffers significant hydrodynamic losses due to fluid rotation, deformation, and friction against enclosing surfaces. These losses are particularly high in the housing and return line, as movement in them is also accompanied by fluid rotation, significantly increasing the friction path. At speeds exceeding 20 meters per second, these losses account for almost half of the total energy consumption.
[0005] The rotation of the liquid causes losses due to its additional multiple participation in friction against the internal surfaces of the housing due to the emergence of a counter-axial Rossby flow.
[0006] Another significant drawback of this technical solution is the relatively long return line with two turning sections. This creates additional hydraulic losses, reducing the efficiency of the heat generator.
[0007] A device for heating a liquid is known (patent of the Russian Federation No. 2609553, class F 24 J3 / 00, 2015), including a heat generator containing a cyclone in the form of a snail with a tangential inlet pipe and a central outlet opening connected to a housing made in the form of a pipe with a braking device, a power pump connected to the inlet pipe of the heat generator and a return pipeline, which can be made in the form of a second heat generator with a power pump, installed in series with respect to the first heat generator.
[0008] This return pipeline design eliminates hydraulic losses associated with flow turns and frictional losses to potential flow in straight sections of the return pipeline. However, this design also results in significantly greater hydraulic energy losses in the second heat generator casing, due to the replacement of potential flow in the return pipeline by vortex flow within the second heat generator casing. This vortex flow also accounts for almost half of the total energy consumption of the second heat generator's operating process.
[0009] The closest technical solution to the claimed one is, and is adopted as a prototype, a vortex cavitator (patent of the Russian Federation for utility model No. 190168, cl. F 25 B9 / 04, 2018), containing a cyclone, the first end wall of which has a central outlet, the second end wall is blind, and the shell is equipped with a tangential inlet pipe, a vane pump with suction and discharge pipes and an impeller rotating along the tangential inlet pipe of the cyclone, as well as inlet and outlet pipes, the cyclone is coaxially connected with the central outlet directly to the suction pipe of the vane pump, and the tangential inlet pipe of the cyclone and the discharge pipe of the pump have opposite orientation and are connected by a return pipeline.
[0010] Connecting the cyclone with its central outlet port coaxially directly to the suction port of the vane pump and connecting the tangential inlet port of the cyclone and the discharge port of the vane pump via a return pipeline with their opposite orientation (Fig. 3) allows for a reduction in power consumption. In this case, the cyclone creates a rotation of the liquid flow in the same direction as the impeller of the vane pump, and when this flow enters the vane pump from the cyclone, it is already pre-twisted to catch up with the impeller blades of the vane pump. The difference in peripheral speeds between the liquid entering the pump and the impeller blades for such a pre-twisted flow is reduced, consequently, the load on the blade will decrease, the torque on the shaft and the power consumption will decrease, and consequently, its efficiency will increase (Fig. 4).On the other hand, the energy transferred to the fluid by the pump decreases, but the sum of the specific energies—introduced by the pre-swirled fluid and transferred by the impeller of a vane pump—reaches the required, i.e., rated value. The impeller's peripheral speed remains constant, since the peripheral speed of the fluid at the trailing edges of the vanes cannot be less than the impeller's speed in this case. Consequently, the pump outlet pressure will not fall below the rated value (Fig. 5, Fig. 6).
[0011] The result of implementing the features under consideration is achieved by the fact that the energy from the flow remaining from the previous cycle (as the fluid moves along the trajectory of vane pump - cyclone - vane pump - etc.) is returned to the vane pump each time, and the pump itself only needs to add the portion of this energy missing to reach the nominal value. Moreover, the smaller the energy loss in the circuit, the less energy is required to replenish it.
[0012] However, a unique feature of the design under consideration is that the return line must have a bend at an angle of at least 180°, which can be achieved either by two rectangular elbows or by bending the return line at this angle. The bend (in both cases) presupposes the formation of two conjugate vortices with longitudinal axes due to the flow core impacting the inner surface of the outer wall of the curved pipe, reflecting off it and splitting into two parts, each of which, along its inner lateral surface of the pipe, moves to smaller bending radii, followed by their closure and multiple repetition of all phases of the cycle under consideration (Fig. 7).
[0013] When a flow with such a structure enters the cyclone through the inlet tangential pipe, it affects the sound generation mechanism, disrupts the phase synchronism of the interacting flows in the cyclone, therefore, reduces the amplitude of the waves, creates noise, and this reduces the intensity of the acoustic cavitation process and also requires an increase in power consumption.
[0014] To eliminate these negative phenomena, the prototype provides for the supply of a connecting pipeline before entering the tangential branch pipe of the cyclone with a flow straightener, for example, in the form of plates connected in a star-shaped manner along the axis of the pipeline.
[0015] However, in this case, the longitudinal plates, firstly, cause additional hydraulic losses, both due to friction against them and due to flow deformation. Secondly, at the outlet of the straightener, the flow is far from fully converted into potential flow. Furthermore, the straight section of the return pipeline also causes additional hydraulic losses due to friction.
[0016] On the other hand, the actual operation of heat generators, including vortex cavitators, requires backup heat generators, which are activated either during maintenance or repair of the primary units, or when operating alongside the primary unit during peak load hours. Having multiple vortex cavitators provides additional redundancy, both for process flexibility and for further design development and increased efficiency.
[0017] The task of the present stage of technological development, in addition to improving traditional technology, is:
[0018] 1) creation of actuators and working bodies based on new physical principles of action;
[0019] 2) create, on the basis of such primitive devices, considering these devices as multifunctional technical systems, special modifications for various purposes;
[0020] 3) development and improvement of the obtained technical systems from the standpoint of possible multivariate changes in their structures, which is the subject of the proposed technical solution.
[0021] Acoustic-cavitation technologies are currently particularly relevant, since by achieving high energy densities at the moment of collapse of cavitation caverns, it is possible to obtain and modify forms of energy, control changes in the properties of water and other liquids, and process solid and gaseous components in liquid media.
[0022] The purpose of the proposed technical solution is to increase the efficiency of the working process of the vortex cavitator by applying a paired structure of their technological use.
[0023] To achieve the stated goal, a known vortex cavitator, comprising a cyclone, the first end wall of which has a central outlet opening coaxially connected directly to the suction branch of a vane pump, which also has an impeller and a discharge branch, the second end wall is blind, and the shell is provided with a tangential inlet branch installed along the rotation of the impeller, as well as supply and discharge branches, is provided with a similar additional vortex cavitator, the discharge branch of the vane pump of which is connected to the inlet branch of the cyclone of the original vortex cavitator, and the vane pump of the original vortex cavitator is connected by a discharge branch to the tangential inlet branch of the cyclone of the additional vortex cavitator.
[0024] In this case, the discharge pipe of the vane pump and the tangential inlet pipe of the cyclone of one of the vortex cavitators can be equipped with a bypass pipeline with shut-off and control valves.
[0025] The provision of the initial vortex cavitator with an additional similar vortex cavitator instead of a return pipeline ensures, firstly, the elimination of hydraulic losses from the system under consideration associated with the return pipeline in the prototype.
[0026] Secondly, the power consumption of each vortex cavitator is reduced, which doubles the efficiency of the entire technical system.
[0027] Thirdly, the flexibility of the technological process is increased. For example, in space heating, either one of every two vortex cavitators can be used by disabling one and activating a bypass line, or, if heating requirements are increased, both vortex cavitators can be used. Moreover, in the latter case, a synergistic effect is achieved: along with the ability to activate a second vortex cavitator and double the useful thermal power, input energy costs are significantly reduced.
[0028] In this case, the working fluid of the original vortex cavitator, swirling in the cyclone, directly hits the impeller blades of the vane pump of the additional vortex cavitator with a peripheral velocity component close to the peripheral velocity of the impeller, which reduces the energy exchange between the impeller and the fluid and thereby significantly reduces the power consumption (Fig. 4; dotted line). This circumstance is true for each of the two vortex cavitators under consideration. Moreover, the reduction in power consumption N тандем < N ул-нас Compared to the prototype, due to the replacement of the return pipeline with an additional vortex cavitator for a tandem unit of vortex cavitators, it has a double value.
[0029] This last circumstance makes it possible to install less expensive, lower-power motors on vortex cavitators (provided they operate together). However, this does not preclude the unit being equipped with motors of the nominal initial power. In this case, when each vortex cavitator is used individually, each motor will consume and deliver its full power, while in tandem, both will consume less energy.
[0030] Reduced energy consumption, due to both the reduced load on the vane impeller of a vane pump and the elimination of hydraulic losses by removing the return line, results in increased power reserve in the drive, for example, an asynchronous electric motor. Increasing the power reserve in an asynchronous electric motor reduces the slip of the motor rotor relative to the rotating magnetic field. Consequently, the rotational speed of the motor rotor, and therefore the impeller of the vane pump, approaches the rotational speed of the magnetic field, i.e., increases. This circumstance leads to an increase in the pressure developed by the vane pump. The increased pressure in this case is realized in the enhanced cavitation capabilities of the device and in an increase in its calorific value (Fig. 8).
[0031] As a result, the quality indicators of the work process in question:
[0032] power consumption value;
[0033] the difference in pressure between the pump inlet and outlet, which is an estimate of the specific energy imparted by the pump to the liquid;
[0034] The liquid heating temperature value (the difference between the outlet and inlet of the cavitator), which is an assessment of the cavitator's cavitation properties, offers advantages over the prototype. Moreover, when vortex cavitators are used as part of a unit, these advantages are twofold.
[0035] The proposed technical solution is explained by the following graphic illustrations:
[0036] Fig. 1 - mechanism of formation of elastic waves in a cyclone;
[0037] Fig. 2 - mechanism of acoustic cavitation;
[0038] Fig. 3 - cross-section of the cyclone of the prototype vortex cavitator with a return pipeline;
[0039] Fig. 4 - dependence of the change in consumed power on the value of transit flow for the proposed design of a vortex cavitator (dashed line N тандем ), for prototype N ул-насand for the analog with a fixed body N полн ;
[0040] Fig. 5 - dependences of the change in the pressure difference at the outlet and inlet of the vane pump at different rotation frequencies of the impeller of the vane pump (at q тр =0.2272 l / s) for the proposed design of the vortex cavitator (dashed line p тандем ) and for the prototype p ул-нас ;
[0041] Fig. 6 - dependences of the change in the pressure difference at the outlet / inlet of the vane pump on the value of the transit flow rate for the proposed design of the vortex cavitator (dashed line p тандем ) and for the prototype p ул-нас at the impeller rotation frequency ƒ=50 Hz;
[0042] Fig. 7 - flow structure in pipeline turns;
[0043] Fig. 8 - dependences of the change in thermal power at different rotation frequencies of the impeller of a vane pump (at q тр =0.2272 l / s) for the proposed design of the vortex cavitator (dashed line Δt тандем ) and for the prototype Δtул-нас ;
[0044] Fig. 9 - longitudinal section through the cyclone of the proposed design of the vortex cavitator;
[0045] Fig. 10 - cross-section of the proposed design of a vortex cavitator;
[0046] Each of the two vortex cavitators - the initial and the additional one, connected in tandem into one unit contains (Fig. 9, Fig. 10) a liquid movement accelerator made in the form of a cyclone 1, the first end wall 2 of which has a central outlet 3, the second end wall is blind 4, and the shell 5 is equipped with a tangential inlet pipe 6, a vane pump 7 with an impeller 8, blades 9, suction 10 and discharge 11 pipes, supply 13 and discharge pipes 14. In addition, in each of the vortex cavitators, the impeller 8 is installed in the vane pump 7 on the drive shaft 15.In this case, the cyclone 1 of each vortex cavitator is coaxially connected directly with the suction branch pipe 10 of the vane pump 7 by the central outlet opening 3, the pressure branch pipe 11 of the vane pump 7 of the additional vortex cavitator is connected with the inlet branch pipe 6 of the cyclone 1 of the initial vortex cavitator, and the vane pump 7 of the initial vortex cavitator is connected by the pressure branch pipe 11 with the tangential inlet branch pipe 6 of the cyclone 1 of the additional vortex cavitator. The tangential inlet pipes 6 of the cyclones 1 are installed in the same direction as the rotation of the impellers 8 of the vane pumps 7. Also, the inlet pipe 13 is tangentially connected to the suction pipe 10 of the vane pump 7 in the same direction as the rotation of the impeller 8, the outlet pipe 14 is connected to the second blind end wall 4 of the cyclone 1 coaxially with the central outlet opening 3 of the first end wall 2.
[0047] In addition, the discharge pipe 11 of the vane pump 7 and the tangential inlet pipe 6 of the cyclone 1 of one of the vortex cavitators can be equipped with a bypass pipeline 16 with shut-off and control valves 17.
[0048] The tandem vortex cavitator unit operates as follows. Before startup, the internal volumes of each vane pump 7 and cyclone 1 are filled with water under pressure through the inlet pipe 13. Air is then expelled through the outlet pipe 14. Upon startup, the impeller 8 of each vane pump 7 begins to rotate via the drive shaft 15 (electric motor - not shown in the figures). It uses the blades 8 to set the impeller in motion and accelerate the water in the circumferential and radial directions, creating a vacuum in the suction pipe 10 and water pressure in the discharge pipe 11. Due to the difference in these pressures, water is set in motion in cyclone 1; it flows from vane pump 7 through pressure pipe 11, for example, of the initial vortex cavitator into tangential pipe 6 of cyclone 1 of the additional vortex cavitator.The liquid then moves along the inner surface of shell 5 in cyclone 1 of the additional vortex cavitator, losing a slight amount of velocity and therefore expanding in cross-section. Consequently, a centripetal component appears, increasing as the main flow moves along shell 5. When this portion of the flow reaches the confluence with the inlet from the outlet tangential nozzle 6, these parts compete with each other, alternately pressing against each other, thereby creating elastic (acoustic) waves that generate periodic cavitation and thereby heat the water.
[0049] The amplitude of oscillations increases with the increase of the input pressure on the tangential branch pipe, in addition, the difference in pressure at the input and output of cyclone 1 determines the magnitude of the liquid velocity in cyclone 1, therefore, its growth increases the frequency of the generated sound waves.
[0050] After performing the positive function after interacting with the inlet flow, the working fluid (water) leaves the cyclone 1 of the additional vortex cavitator through the central outlet 3 in a rotating axial flow and enters the suction branch 10 of the vane pump 7 of the initial vortex cavitator. In the vane pump of the initial vortex cavitator, the flow with a preliminary swirl (obtained in the cyclone 1 of the additional vortex cavitator) hits the blades 9 of the impeller 8 rotating in the same direction, receives from them additional kinetic energy, which is converted at the outlet from the blades 9 into hydraulic pressure, and, rushing from the discharge branch 11 of the initial vortex cavitator into the tangential inlet branch 6 of the additional vortex cavitator, again participates in subsequent cycles.
[0051] The considered variant of the tandem use of vortex cavitators assumes a significant saving of the expended energy, since when entering through the central opening 3 of the first end wall 2 into the suction branch 10 of the vane pump 7 in each of the vortex cavitators, the liquid has a significant vortex component and only slightly lags behind the rotating blades 9 of the impeller 8. Consequently, the hydrodynamic force of interaction between them in each of the vortex cavitators, proportional to the square of the difference in peripheral speeds, is insignificant, therefore the torque on the drive shaft 15 is small. As a result, the product of the force by the arm of the point of its application and by a given constant rotational speed determines the minimum consumed power, that is, provides its savings (Fig. 4).
[0052] Thus, replacing the passive return pipeline in the prototype (Fig. 3) with an active equivalent in the form of a second vortex cavitator, firstly, multiplies this savings and, secondly, eliminates the energy costs of overcoming hydraulic resistance in the return pipeline of the prototype (Fig. 3).
[0053] By eliminating the hydraulic losses associated with the prototype's return pipeline, the difference in pressure at the inlet and outlet of the vane pump will exceed that of the prototype (Fig. 5, Fig. 6). Moreover, one of the reasons for the pressure increase relative to the rated value is the circumstance of reduced slip in the drive's asynchronous motor, since a decrease in the torque on the drive shaft 15 in this case contributes to an increase in the rotational speed of this shaft 15, up to the rotational speed of the magnetic field in the electric motor (ƒ=50 Hz). An increase in the rotational speed of the impeller leads to an increase in the pressure in the discharge pipe 11, and in the overall pressure. That is, the balance of the reduction in torque on the drive shaft 15 of the vane pump 7 also includes energy savings from the elimination of the hydraulic losses associated with the prototype's return pipeline (Fig. 3).
[0054] In these cases, increased pressure is realized in the enhancement of the cavitation capabilities of the device and an increase in its calorific value (Fig. 8).
[0055] This option for operating vortex cavitators allows for the installation of lower power drives, i.e., less expensive and more readily available motors.
[0056] Another positive circumstance of tandem operation of vortex cavitators is the increased flexibility of their technological use.
[0057] For example, in heating rooms, either one of every two vortex cavitators can participate by turning off the power supply to the other and turning on the bypass line 16 with valve 17, or, in case of increased heating requirements, both vortex cavitators can participate (with the bypass line closed).
[0058] In the first case, that is, when each of them operates separately, a drive with rated, unreduced power will be required, since the positive effect of pre-swirling the flow at the inlet of vane pump 7 will be eliminated. However, the same drive with rated power in a tandem connection and operation will consume a reduced amount of energy.
[0059] The result is a cost-effective device that is comparable to the prototype in terms of functionality and offers significant advantages in terms of application technology and operating costs. Consequently, the stated goal of the technical solution has been achieved.
[0060] The use of the proposed design variant of the vortex cavitator will reduce the cost of the thermal energy it generates and make its cost comparable to the generation of heat from the combustion of natural gas.
Claims
1. A vortex cavitator comprising a cyclone, the first end wall of which has a central outlet opening coaxially connected directly to the suction branch of a vane pump, which also has an impeller and a discharge branch, the second end wall is blind, and the shell is provided with a tangential inlet branch installed along the rotation of the impeller, as well as supply and discharge branches, characterized in that it is provided with a similar additional vortex cavitator, the discharge branch of the vane pump of which is connected to the inlet branch of the cyclone of the original vortex cavitator, and the vane pump of the original vortex cavitator is connected by a discharge branch to the tangential inlet branch of the cyclone of the additional vortex cavitator.
2. A vortex cavitator according to paragraph 1, characterized in that the discharge pipe of the vane pump and the tangential inlet pipe of the cyclone of one of the vortex cavitators are equipped with a bypass pipeline with shut-off and control valves.