UA66334C2 - Method to obtain heat for heating buildings and constructions and cavitation heat generator with continuous operation - Google Patents

Abstract

Group of inventions relates to generation of heat with cavitation generator for heating buildings and constructions. One forms vortex water flow and provides cavitation mode of its flow at resonance amplification in flow of acoustic and percussion vibrations. One adds to water ethylene-glycol in amount of 7% of water mass with saturation of flow of working liquid with air that is 0.002 of water volume. Heat generator has accelerator and conical splitter of working liquid, at least three accelerators-activators of working liquid, cavitators with placed in radial positions openings, Laval nozzles, cavitators in central and output openings, those are at least five in number. The inventions promote simultaneous heating of working liquid and its feeding to heating system.

Description

The invention relates to thermal power engineering and can be used for autonomous heating of buildings and structures of various purposes, water heating for industrial and domestic needs.

Known devices for heating a liquid, which contain a heat generator with an input and output of a working fluid, a pump connected to the input of a heat generator, an accelerator of fluid movement, a tubular part with a braking device at the output of a heat generator with which a return pipeline is connected.

ISA 7205A, gB25829/00, 30.06.1995, Byul.Me2; VO 2045715 SI, E25829/00, 10.10.1995, Bull. Me28).

The principle of operation of known devices is based on the use of pressure drops of the working fluid, as well as on the use of cavitation processes that occur in the flow of liquid and lead to an increase in its temperature.

The closest analog to the invention is a device for heating a liquid, which contains a heat generator with an inlet and outlet of a working fluid, a pump connected to the inlet of the heat generator, an accelerator of fluid movement, supply and return pipelines, a tubular part with a brake device at the outlet of the heat generator with which connected return pipeline, injection nozzles, sequentially located unidirectional conical nozzles, bushings with cylindrical channels, conical liquid splitter.

ISHA 22003 A, P25829/00, 04/30/1998, Bull. Meg2

The disadvantages of the known device are the low efficiency of heat release under the conditions of increasing the volume of the working fluid, the low speed of the diffusion process that occurs in the working fluid, which limits the technical capabilities of the device. 1. The invention is based on the task of improving a device for heating a liquid, in which, by changing its design and supplementing it with new devices, the production of a large amount of thermal energy, the intensification of the diffusion process, and the continuity of the action of the cavitation heat generator for heating the working fluid of a significant volume and simultaneous supply are ensured it into the supply pipeline.

The task is solved by the fact that the cavitation heat generator of continuous action with the input and output of the working fluid, the pump, supply and return pipelines, according to the invention, additionally contains the accelerator-activator of the working fluid (Fig. 2), connected to the pump (35) and the transition with a liquid supply nozzle (33), consisting of at least three serially connected nozzles with different diameters of passage channels, connected to each other by means of flanges for changing the direction of the main flow of liquid (27), with a conical bevel and an ejection acceleration channel (29) , located tangentially to the passage channel of the nozzle (26). The accelerator-activator of the working fluid is additionally supplemented with cavitators (24, 31) with radially located holes that generate a flow of calibrated cavitation bubbles that enter the slotted flow zone for the purpose of crushing the cavitation bubbles and creating their secondary flow.

The accelerator-activator of the working fluid is additionally equipped with a slotted ejector (23) and a chamber of increased pressure of the working flow (1), which has a slotted ejector accelerator channel located tangentially to the passage channel of the central nozzle (2) of the heat generator (Fig. 1). The central nozzle (2) of the heat generator is connected to its central part (7), which contains a cavitator (3) with radial holes (4), which generate a flow of calibrated cavitation bubbles, and has radial channels (5) in the gap zone of the flow. The cavitator (3) also has a Laval cavitating nozzle (6), which provides instant narrowing and expansion of the main liquid flow and contributes to the formation of a secondary flow of crushed cavitation bubbles.

The cavitation heat generator of continuous action additionally contains distribution flanges (10, 11) of the main fluid flow with a conical splitter, which, under pressure, evenly distributes the working fluid through slotted tangentially directed channels (12, 13) to the channels of the output nozzles (14) of the heat generator, concentrically located from the central the nozzle (2) of the heat generator, of which there are at least five, and the supply pipeline (21) of the heating system or supply of hot water to consumers. The outlet nozzles (14) are equipped with cavitators (15) with radially located holes (16) that generate a flow of calibrated cavitation bubbles, annular channels (17) in the body of the nozzles (19) and Laval cavitation nozzles (18) that grind the cavitation bubbles. Outlet nozzles (19) are additionally equipped with nozzle outlets (20) of the heat generator, which have an angle of inclination of 45" to the axis of the nozzle and are directed away from the central nozzle (2) of the heat generator.

The cavitation heat generator of continuous action together with the described devices works as follows.

The flow of water with the help of the pump (35) enters the passage channel of the nozzle (32) of the accelerator-activator (Fig. 2) at a speed of 7 m/s, then it enters the conical part of the static cavitator (31), where it twists and gains speed up to U9 m/s. At this speed, the liquid flow enters the internal channel of the static cavitator (31), the diameter of which is 2.4 times smaller than the diameter of the passage channel of the nozzle (32), while the liquid flow speed increases to 14 m/s. The internal channel of the static cavitator is impenetrable, so the main flow, reaching its conical end, additionally twists and acquires reverse motion, while the primary process of cavitation bubbles formation occurs due to turbulence and heat release due to the conversion of kinetic energy of the flow into thermal energy. Next, through two rows of radial holes, which are generators of a uniform flow of calibrated cavitation bubbles of the same diameter, the main flow sharply changes the direction of movement, during which additional heat energy is released, enters the slit zone of the flow at a speed of up to 24 m/s and enters the radial channels of the nozzle (30), where there is an active process of cavitation bubbles collapsing with the release of energy and a local increase in the speed of cumulative jets up to 700 m/s and the crushing of primary bubbles into their saturated flow with smaller diameters up to 20-25 μm. At the same time, in the gap formed by the outer diameter of the static cavitator (31)-ak, and the inner diameter of the nozzle (30)-O, according to the formula:

Where

Mve 02-M (02-Y).

Where

F - - entrance -yi- - 084

B) M 24

Where: Mach - the input speed of the liquid flow, which is given to it by the pump;

M is the speed of the liquid flow, which it acquires at the entrance to the slot gap; ak o. coefficient of continuity (compression) of the flow of the air-water mixture, an air-water mass of bubbles arises, which is compressible (unlike a liquid), with a volumetric air content of 0.8, which leads to the emergence of additional shock waves and supersonic flow. The speed of sound for an air-water mass is calculated by Wood's formula:

R ah shle 941 - osdrr where: R - pressure in the air-water mixture; o - volume content of air; yr. volumetric g and the mouth of the liquid

Thus, co-0.8; o(1-o)-0.16; and the speed of sound for this medium is 25 m/s.

For further activation of the process of heat generation due to the occurrence of shock waves of ultrasonic and shock cavitation, when bubbles with a diameter of up to 20-25 μm are closed during their slamming, a supersonic flow speed is required for the air-water mixture, which is achieved in the slot gap and in the Laval cavitating nozzle. located at the end of the static cavitator (31), which provides instant narrowing and expansion of the main liquid flow. Next, the main flow of liquid enters the flow part of the high-pressure channel of the nozzle (30), where the microbubbles are completely point-clamped without the formation of cumulative jets, and thus intensive heating of the liquid occurs.

Next, the main flow of liquid enters the conical channel of the nozzle (28), where again its speed increases to 5 m/s and to the cylindrical through channel of the nozzle (28) with a diameter equal to 0.5 the diameter of the through channel of the nozzle (32), where its speed increases up to 9 m/s and there is a sharp change in the flow direction due to the guiding conical bevel of the flange (27) into the ejection accelerating channel (29), which is located tangentially to the passage channel of the nozzle (26), while the speed of the main liquid flow increases to 14 m/s . When the flow passes through the pipe (26) channel, it twists and as a result heat energy is released. Further, the main flow of liquid enters the conical channel of the nozzle (25), where it again acquires a speed of U9m/s and enters the internal channel of the static cavitator (24), where the same physical phenomena occur as when passing through the flow of the static cavitator (31) with the release thermal energy. Later, when passing through the nozzle (28), the flange for changing the direction of flow and channels (26, 25) and the static cavitator (24) of the nozzle (22), the temperature of the main liquid flow increases sequentially.

At the exit of the accelerator-activator (Fig. 2) a slot ejector (23) with holes is installed, when passing through which the main flow is accelerated and cavitation bubbles are formed, which are closed in the high pressure chamber (1) and thermal energy is released. Through the slotted ejector accelerator channel, located tangentially to the passage channel of the nozzle (2), the main liquid flow with a speed of 9 m/s enters the passage channel (2) of the central nozzle of the heat generator, swirls and heat energy is released. When the main flow passes through the static cavitator (3) and bubble-generating holes, radial channels (5) and Laval nozzles (b), heat energy is also released and the flow enters the conical channel of the nozzle (8), where it is twisted and heat energy is released again . When the main flow of liquid enters the distribution flange (10) with a conical splitter, the main flow is divided into flows that enter the slotted tangentially directed channels (12, 13) to the flow channels of the outlet nozzles (14), of which there are at least five, and the flow channel of the supply pipeline (21) of the heating system or hot water supply to consumers and acquires a speed of Zm/s.

The location of the entrance of the slit channels (12, 13) relative to the nozzles (14, 21) is shown in Fig. 4, 5 for the northern and southern hemispheres, which is related to the action of the Earth's magnetic field on water, which is diamagnetic and has a magnetic susceptibility of 13.0 10 during the spiral movement of the main flow, directed in the same direction as the action of the vector of the intensity of the Earth's magnetic field in different hemispheres, in order to increase the speed of the main flow. In addition, the Coriolis force will act on the liquid flow rotating in the outlet nozzles (14), which will deflect the outer layers of the liquid in the direction perpendicular to its relative speed and exert pressure on the walls of the passage channel of the nozzles (14), which will cause the release of thermal energy.

The cross-sectional area of the slit channel (13) depends on the volume of the heat carrier, which must be supplied to the supply pipeline (21) and is a variable value, thereby regulating the rate of supply of the heat carrier.

After that, the liquid flow enters the internal flow channels of the static cavitators (15), passes through the radial channels (16), the slotted flow zone with annular channels (17) in the body of the nozzles (19) and the Laval cavitation nozzles (18), while the following occurs the same physical processes and release of heat energy, as when the liquid flow passes through the static cavitators of the accelerator-activator (Fig. 2) and the central nozzle (2) of the heat generator. When the liquid flow passes through the nozzle exits (20) of the nozzles (19), which have an angle of inclination of the ribs of 45" to the axis of the nozzle, additional thermal energy is released and the total area of the diffusion process increases by five times compared to the designs of heat generators with one nozzle outlet of the working fluid .

Thus, the task of improving the device by changing the design and adding new devices ensures the production of a large amount of thermal energy by the cavitation heat generator for heating a significant volume of liquid and the continuity of its action with simultaneous feeding into the supply pipeline.

The cavitation heat generator of continuous action, according to the present invention, can be used for autonomous heating of buildings and structures of various purposes, in agriculture, in technological production processes, or for energy generation.

A change in the number of elements of the accelerator-activator and the number of nozzles for the output of the working fluid, which are located concentrically with respect to the central nozzle of the heat generator, or a change in the cross-sectional area of the channel of the supply pipeline is obvious to specialists in this field and cannot be the basis for improving the device according to the present invention. 2. The method of obtaining heat for heating buildings and structures.

The invention belongs to thermal energy, in particular to methods of obtaining heat, which occurs differently than as a result of burning fuels.

There are known methods of heating the liquid, in which heat is obtained due to the action on the main flow of the liquid of jet counterflows, or mechanical obstacles located in the path of the flow of liquid, or due to the use of heat generators of periodic action on a limited volume of the heat carrier, or reducing the volume heat carrier with an increase in energy consumption for heating the liquid, or by adding heavy water to the main liquid flow.

The closest to the claimed method is the method of obtaining heat with the help of devices for heating liquid - heat generators, which are described in (patents NVO 2045715 SI, P25829/00, 10.10.1995, Bull. Me28 and SHA 47535 02, P2423/00, 07/15/2002, Bul. Me7|.

According to this method, water of any purity (for example, technical) using a pump, which develops a pressure up to 1000 m, is fed to the input of the heat generator described in (patent VO 2045715 СИ, Е 25829/00) and with its help, the water of the total mass is heated 200 kg. in a closed loop with an initial temperature of 18 - 202С to a temperature of 709Сb using a pump with a power of 5.5 kW. The thermal performance of the heat generator is not indicated in the patent, and the efficiency is indicated without providing information about the temperature of the outside air, the thickness and material of the walls of the premises that were heated using this device and method, and the indicated rate of periodic heating of the liquid in a closed circuit, which is a discrepancy of 1.570 per a minute

In the method of obtaining heat using the same device specified in (patent OA 47535 C2,

E2423/00, 15.07.2002, Bull. Me7|, the task was set in the method of obtaining heat by changing and specifying the temperature interval of the water used for heat production in the heat generator, to ensure an increase in the efficiency of heat production.

The task was solved by illustrating the given examples, in which water was pre-heated to a temperature of 63-702C using an electric heater or a heat generator with the same technical characteristics. After that, the working circuit of the same heat generator was filled with this heated water and after its operation in a closed cycle, a heating rate of 0.820 per minute was obtained, up to the boiling temperature of water. In another given example, the power of the electric motor is increased to 11 kW. that is, water of the same total weight of 100 kg with a temperature higher than 6320 is poured into the working circuit of the heat generator twice. At the same time, as stated in the patent, the efficiency of the heat generator has reached 2.

In this way, the task set in the patent in its first part proved beyond doubt that the intensity of water heating increases upon reaching a temperature higher than 63"C and continues up to the boiling state, but in the second part of the task, real calculations of the efficiency of heat production took place without taking into account previous energy costs for heating water to a temperature higher than 6370.

When using a more powerful pump and reducing the mass of water by half, relative to the previous patent, the efficiency of the device increased. Thus, it is confirmed that the intensity of heating of the working fluid in a closed loop primarily depends on the increase in the rate of circulation of the flow in the device per unit of time, that is, the intensification of cavitation and shock wave processes.

The disadvantages of the known method are the low efficiency of heat release under the conditions of increasing the volume of the working fluid without increasing the power of the pump and the frequent periodicity of supplying the heat carrier (water) to the water heating system of rooms with an operating temperature of 70"C, where it gives off part of its heat and returns to the input of the heat generator with a temperature of 65-67" and thus leads to frequent switching on of the pump, i.e. energy consumption and wear of the feed pump, the inability to maintain the temperature of the coolant in the heating system for a long enough time, as well as the impossibility of using the method and device in technological processes that require temperature superheated water.

The invention is based on the problem of a method of obtaining heat, which involves increasing the efficiency of obtaining heat under the conditions of increasing the total mass of the heat carrier without increasing energy consumption, and a method by which it is possible to simultaneously supply the heat carrier to consumers and heat it using one heat generator.

The task is achieved by adding ethylene glycol (ethanediol) HOCH» - CH2OH in the amount of up to 7905 in the solution, the boiling point of which is 114702 under normal conditions, to the water that is in the closed circuit-tank for the coolant (36). The total volume of the coolant in the container (36) consists of the volume required to fill the heating system and heat exchangers (44), plus an additional volume of water equal to 0.7 of the volume of the heating system and shown in Fig. 9 dashed - 1st water level.

The presence of ethylene glycol in the water provides, in addition to the possibility of raising the boiling temperature of the working fluid, it also contributes to the continuity of the air-water phase under the conditions of increasing the flow speed to supersonic in the crevice space of the accelerator-activator and the heat generator, and ensures that the heating system does not freeze in emergency circumstances when the heat generator is turned off.

Also, the achievement of the goal of the method of increasing the efficiency of obtaining heat occurs due to the use of an additional device, which is a tube made of stainless steel (39), the upper end of which goes into the space of the air cap of the container for the coolant (36), and the lower end is immersed in the intake pipe (34 ) of the pump (35) and has vertical holes (53) in the lower part, located evenly along the perimeter of the tube, and which do not extend in height beyond the intake pipe (34) of the pump (35). The presence of this device makes it possible, by injecting the appropriate amount of air together with the flow of the working fluid into the heat generator system, to intensify the heat exchange process due to the saturation of the fluid flow with air nuclei of the flow of cavitation bubbles and a decrease in the partial pressure of water, which in turn affects the intensity of heat transfer, which under such conditions increases to 2095 in the heat generator, and an additional increase in the boiling point of the working fluid by 595 - to 12070.

In this way, the set task of the method of obtaining heat is achieved, which involves increasing the efficiency of its obtaining and raising the boiling level of the working fluid without changing the atmospheric pressure.

The second part of the task involves a method by which the simultaneous supply of heat carrier to consumers and its heating with the help of one heat generator is achieved.

The task is achieved by the fact that the capacity of the working fluid (36) has a layer of material with a low specific heat transfer coefficient, according to the necessary calculation, and allows maintaining the temperature of the heated coolant for a long time without a significant decrease in its temperature. The capacity of the working fluid (36) is structurally designed in such a way that it has two compartments with a partition (37) made of a material with a low heat transfer coefficient, and they are connected to each other by a passage for the working fluid (38) in the lower part, and are also connected through a partition ( 37) in the space of the air cap of the tank (36) with the help of a steel tube, which makes it possible to equalize the pressure balance in the tank compartments and maintain the same level of the working fluid in the tank. The presence of two compartments makes it possible to heat the working fluid in which the heat generator is located more actively, and to prevent a long process of diffusion on a large mass of heat carrier. In the other part, there is a working fluid with a lower temperature, which is taken by the intake pipe (34) of the pump (35) together with air in a ratio of 0.002 volume from the mass of the intake working fluid, which passes in a unit of time through the intake pipe of the pump, which supplies water to of the heat generator from the passage channel (38).

The heat generator (10) and the container for the working fluid (36) are connected to the heating system (or hot water supply) through the discharge nozzle (21) and the return pipe (45), which enters through the flange in the area of the air cap of the container for the working fluid, but does not touch its surface. The container is also equipped with a thermocouple (40) for reading the temperature of the working fluid and control and management through the unit of control and regulation devices (49) with a normally closed electrohydraulic valve (41). The container for the working fluid (36) is additionally equipped with a tap (51) for supplying the system with working fluid when necessary, or it can be used by connecting to the water supply network for continuous water supply to the container. A tap (52) located in the lower part of the container is provided for draining the working fluid from the container.

In order for the system to be independent from the central power supply networks and in case of its emergency shutdown, a diesel generator (54) of the required capacity is provided, which is connected to the pump and to the unit of control and regulation devices (49). The system is also equipped with valves with manual control for exiting the system to the operating mode (42) and manual draining of the working fluid from the heating system and heat exchangers (44).

In order to prevent water hammer, the pipeline system includes a water hammer quenching capacity, which is included after the taps (41,42). The return pipeline is equipped with a thermocouple (46) connected to the block of control and regulation devices (49) and makes it possible to take temperature readings in the return pipeline and to control the normally closed electric hydraulic valve (47) through the block of control and regulation devices. The block of control and regulation devices (49) controls the operation of all system nodes in automatic mode.

The system that implements the method of simultaneously supplying the coolant to consumers and heating it with the help of one heat generator works as follows.

After filling the container (36) with the working fluid in the required amount, as it was indicated earlier, with its initial temperature above 5"C, the pump (35) is turned on, without the participation of the unit of control and regulation devices (49), and the working fluid is heated using of the heat generator to a temperature of 907C, the heating progress is controlled by a thermocouple (40). After reaching a temperature of 9072, the working fluid opens the manual control valve (42) smoothly and the working fluid enters the heating circuit with heat exchangers (44) while the heat generator is turned on, while the valve (48 , 51) should be open.

The thermocouple (46) takes readings of the coolant in the return pipeline (45). After filling the heating system with the working liquid, the valves (42,48,51) are closed, the pump is turned off and the working temperature of the coolant is set on the devices of the control and regulating devices in the supply and return pipelines of the heating system. The upper closing temperature of the electrohydraulic valve (41) is set lower than the temperature of the working fluid 907C in the tank (36), for example 80"C and the synchronous shutdown of the pump (35), the opening temperature of the electrohydraulic valve (47) is set, for example 607C and the automatic switching on of the pump (35) for the start of the heat generator. The temperature 9092 of the opening of the electrohydraulic valve (41) is also set. After that, the pump and the heat generator are automatically turned on. When the temperature of the working fluid in the tank reaches the level of 9072, the valve (41) and (47) opens and the heat generator pumps water into the system, while it continues to heat the working fluid in the container. When the temperature in the return pipeline reaches the level of 807C, the valves (41, 47) are automatically closed, the pump is turned off until the system cooling level is 60"C, after which the valve (47) opens and the pump and the heat generator supplying water are automatically turned on into the system through the open valve (41) after it is properly heated. The time required to reach the temperature of the required heating will be insignificant, due to the fact that the mass of water that comes with a temperature of 60" from the return pipeline (45) is insignificant in comparison with the mass of water that is in the container and has a temperature of lower than 807"C, thus it quickly heats up to a temperature higher than 63"C, at which, as proved in (patent OA 47535 C2, E243/001, a sharp intensification of the heating rate of the working fluid occurs. After heating the working fluid in the container to the temperature 9070 system enters the automatic mode of operation and the entire cycle is repeated in the same order, while the time of operation of the heat generator will depend on the set temperature parameters of the heating system, and the frequency of turning on the heat generator will automatically depend on the temperature of the external environment,

which affects the temperature regime of the heated room.

In this way, the method of simultaneously supplying the coolant to consumers and heating it with the help of one heat generator is implemented.

Changing the parameters of the pump power, increasing or decreasing the total volume of the container for the working fluid and the ratio of its parts, which are variable quantities, as well as the serial connection of heat generator systems according to the given method are obvious to specialists in this field and cannot be the basis for improving the method , according to the present invention.

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Claims (2)

1. The method of obtaining heat for heating buildings and structures by forming a vortex flow of water and ensuring the cavitation regime of its flow with resonant amplification of sound and shock vibrations arising in this flow, which differs in that ethylene glycol is added to the water in the amount of 7 90 by mass of water and saturate the flow of the working fluid with air, which is 0.002 of the volume of water, mix the working fluid, which is in two different compartments of the container (36) of the heat generator with different temperatures (T1-85-115 degrees C, T2-65-95 degrees C) in the passage channel (38), which connects its two departments, as a result of which the diffusion of the working fluid is accelerated and energy consumption is reduced, with the help of the accelerator-activator of the heat generator (30) with cavitators (24, 31), the fluid is saturated with air, which leads to the formation of calibrated cavitation bubbles, which act on the main flow of the working fluid, 1 increase its temperature, the working fluid is passed through the slit gap formed by the external by the diameter of the cavitators 1 by the inner diameter of the nozzles of the accelerator-activator of the heat generator, where they create an air-liquid mass of bubbles in the working fluid, which is compressed in this gap with a volumetric air content of 0.5, which leads to the emergence of additional shock waves of ultrasonic and shock cavitation and creates a supersonic flow of air-liquid mass of bubbles. 2. A cavitation heat generator of continuous action with an inlet and outlet of the working fluid, a pump connected to the inlet of the heat generator, a liquid accelerator, supply and return pipelines, unidirectional conical nozzles, a conical liquid splitter, which is distinguished by the fact that the cavitation heat generator additionally includes the accelerator-activator of the working fluid (Fig. 2), consisting of at least three nozzles with different diameters of the passage channels, connected in series with each other by means of flanges for changing the direction of the main fluid flow with a conical bevel (27) and an accelerating channel (29), and contains inside cavitators (24, 31) with radially located holes (4, 16) for generating a flow of calibrated cavitation bubbles, as well as Laval cavitation nozzles (b, 18), a chamber (1) of increased liquid pressure and cavitators (3, 15) , contained in the central (7) 1 outlet (19) nozzles, of which there are at least five, of the heat generator, distribution flanges (10) of the main of the fluid flow, which flows simultaneously to the outlet nozzles (19) of the heat generator and to the nozzle of the supply pipeline (21), which ensures the continuity of simultaneous heating of the working fluid and its supply to consumers.