US20070152077A1 - Method for producing heat for heating building and constructions and a continuous cavitation heat generator - Google Patents

Method for producing heat for heating building and constructions and a continuous cavitation heat generator Download PDF

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Publication number
US20070152077A1
US20070152077A1 US10/584,796 US58479604A US2007152077A1 US 20070152077 A1 US20070152077 A1 US 20070152077A1 US 58479604 A US58479604 A US 58479604A US 2007152077 A1 US2007152077 A1 US 2007152077A1
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heat
stream
fluid
generator
heating
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Abandoned
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US10/584,796
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English (en)
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Anatoliy Korniyenko
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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
    • F24V99/00—Subject matter not provided for in other main groups of this subclass
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D3/00—Hot-water central heating systems
    • F24D3/02—Hot-water central heating systems with forced circulation, e.g. by pumps

Definitions

  • the invention belongs to heat-power engineering, namely, to methods of getting heat, which originates differently than due to the fuel combustion and may be used for autonomous heating buildings and various purpose constructions, for heating water for industrial and domestic needs.
  • Methods of heating fluid are known, under which heat is got by means of the action of jet counter-current streams on the main fluid stream, or due to mechanical obstacles disposed on the way of the fluid, or by means of using of periodically working heat-generators with the limited volume of heat carrier, or decreasing volume of heat carrier at increasing power inputs for heating fluid or due to adding heavy water to the main stream.
  • the set problem was being settled by illustrating the examples given, under which preliminary heating of water up to the temperature of 63-70° C. was carried out by the instrumentality of an electric heating unit or a heat-generator with the same performance data. Then, the operating circuit of a similar heat-generator was filled with that heated water and after its performance in the closed cycle, the heating temperature of 0.8° C. per minute was acquired, up to the water boiling point. In the other example given, electromotor capacity is increased up to 11 kilowatt, i.e. two times as much and the operating circuit of the heat-generator is filled with water of the same mass of 100 kg with the temperature above 63° C. At that, as it is stated in Patent UA 47535 C2, 15.07.2002, Bul. No. 7 heat-generator operation effectiveness leveled 2.
  • the disadvantages of the currently in use method are insufficient heat generation effectiveness provided increasing of the operating fluid volume without increasing of the pump output and frequent periodicity of heat carrier (water) delivery to a premise hot-water heating system with operating the temperature of 70° C., where it gives away a part of its heat and returns to the heat-generator inlet with the temperature of 65-67° C. and consequently reduces to frequent activations of the pump, i.e. to excessive power inputs, to the delivery pump wear-out, and to the impossibility of keeping of the heat carrier temperature in the heating system for quite long, and also to the impossibility of using of the method and the device in technological operations requiring superheated water temperature.
  • Fluid heating devices which comprise a heat-generator with an operating fluid input and output, a pump connected to the heat-generator inlet, a stream accelerator, and a tubular part with a brake arrangement at the heat-generator outlet, to which a return pipe is connected.
  • the principle of operation of currently in use devices is based on using of operating fluid pressure differential and on using cavitational processes originating in the fluid stream and resulting in increasing of its temperature.
  • the most similar analog of the utility invention is the device for fluid heating comprising a heat-generator with an operating fluid input and output, a pump connected to the heat-generator input, a stream accelerator, feeding and return pipes, a tubular part with a brake arrangement at the heat-generator outlet, to which the return pipe is connected, injection pipes, sequence unidirectional egg-shaped pipes, cylindrically ported bushings with cylinder passages, a conical fluid splitter. (UA 22003 A, F 25 B29/00, 30.04.1998, Bul. No. 2)
  • the basis of the invention is the problem concerning the method of heat getting that provides increasing of heat effectiveness getting, provided, the heat carrier total mass increases without power inputs increasing, and the method by the instrumentality of which the simultaneous heat carrier delivery to consumers and its heating by the instrumentality of the one heat-generator are possible.
  • the problem posed is settled by means of delivering ethylene glycol (ethandiol) HOCH 2 —CH 2 OH at the amount up to 7% in solution, its boiling point being 114° C. under normal conditions, into water in a closed tank for the heat carrier ( 36 ).
  • the heat carrier total volume in the tank ( 36 ) involves the volume necessary for filling of the heating system and heat exchangers ( 44 ), and additional water volume amounts to 0.7 of the heating system volume and indicated in FIG. 9 with dotted line—the first water level.
  • a complementary device being a tube made of stainless steel ( 39 ), the upper end of which goes to the air hood space of the heat carrier tank ( 36 ), and the lower end, is submerged into the intake manifold ( 34 ) of the pump ( 35 ) and possesses vertical holes in its lower part ( 53 ) distributed uniformly along the tube perimeter, but they do not exceed in height the intake manifold limits ( 34 ) of the pump ( 35 ).
  • this device provides the possibility, by means of pumping-in a corresponding amount of air together with the operating fluid stream into the heat-generator system, to intensify the heat exchange due to fluid stream saturation with incipient cavitational air-beads and partial water pressure decrease, that, in its turn, influences the heat transfer rate, which under such conditions increases up to 20% in the heat-generator, and allows extra raising of the operating fluid boiling-point by 5%—up to 120° C.
  • the second part of the posed problem provides the method due to which the simultaneous heat carrier delivery to the consumers and its heating by the instrumentality of the same heat-generator are possible.
  • the posed problem is settled due to the fact that the operating fluid tank ( 36 ) has a layer of material with a low heat conductivity specific coefficient corresponding to the necessary calculation, and allows holding the heated heat carrier temperature without considerable reduction of its temperature for long.
  • the operating fluid tank ( 36 ) is embodied in the following way, it has two sections with a baffle ( 37 ) made of heat transfer low coefficient material, and interconnected by a pass for the operating fluid ( 38 ) in the lower part, and also are connected by a baffle ( 37 ) in the tank air hood space ( 36 ) that makes it possible to equalize pressure balance in the tank sections and to maintain an equal level of the operating fluid in the tank.
  • the presence of two sections makes it possible to heat more actively the operating fluid in which the heat-generator is disposed and to prevent the continuous process of thermodiffusion for large mass of the heat carrier.
  • the operating fluid with lower temperature is placed, which is offtaken by the intake manifold ( 34 ) of the pump ( 35 ) together with air in ratio 0.002 of the volume of the offtaken operating fluid mass, which passes through the intake manifold of the pump delivering water to the heat-generator from the pass ( 38 ).
  • the heat-generator ( 10 ) and the operating fluid tank ( 36 ) are jointed with the heating system (or hot water delivery system) by means of a discharge connection ( 21 ) and return pipe ( 45 ), which enters the tank air hood space zone of the operating fluid through a flange, but does not touch the fluid's surface.
  • the tank is also equipped with a thermocouple ( 40 ) for taking a reading of the operating fluid temperature, and for checking and steering through a control-regulating device assemblage ( 49 ) by a normally closed electrohydrovalve ( 41 ).
  • the operating fluid tank ( 36 ) is additionally equipped with a tap ( 51 ) for the system replenishment with the operating fluid if necessary, or it can be used for connecting to the water-supply system with the purpose of continuous water delivery to the tank.
  • a tap ( 52 ) is provided, which is disposed in the lower part of the tank.
  • a diesel-generator set ( 54 ) of a necessary capacity is provided, which is connected to the pump and the control-regulating device assemblage ( 49 ).
  • the system is also equipped with the manually operated faucets for the system change to the operating mode ( 42 ) and manual discharge of the operating fluid from the heating system and heat exchangers ( 44 ).
  • the tank for hydraulic shock damping is provided ( 43 ), which is placed after the taps ( 41 , 42 ).
  • the return pipe is equipped with a thermocouple ( 46 ) connected to the control-regulating device assemblage ( 49 ) and making it possible to take temperature readings in the return pipe and to manage the normally closed electrohydrovalve operation ( 47 ) by the control-regulating device assemblage.
  • the control-regulating device assemblage ( 49 ) operates all the system modules in the automatic mode.
  • the problem of refinement of the heating fluid device is also posed, in which changing of its construction and supplementing of it with new accessories provide the production of large amount of heat energy, intensification of the thermodiffusion process and continuity of the cavitational heat-generator operation for the heating operating fluid of considerable volume and its simultaneous delivery to the feeding pipe.
  • the continuous working cavitation heat-generator with the operating fluid inlet and outlet, the pump, feeding and return pipe, in accordance with the invention additionally comprises an operating fluid accelerator-promoter ( FIG. 2 ), which is connected to the pump ( 35 ) and to an adapter sleeve for fluid delivery ( 33 ), which comprises at least three successively connected manifolds with passes of different diameters, which are interconnected with flanges of the main fluid stream direction change ( 27 ), with conical cant and ejection accelerating passage ( 29 ) disposed tangentially to the manifold pass ( 26 ).
  • an operating fluid accelerator-promoter FIG. 2
  • an adapter sleeve for fluid delivery which comprises at least three successively connected manifolds with passes of different diameters, which are interconnected with flanges of the main fluid stream direction change ( 27 ), with conical cant and ejection accelerating passage ( 29 ) disposed tangentially to the manifold pass ( 26 ).
  • the operating fluid accelerator-promoter is additionally equipped with static cavitators ( 24 , 31 ) with radially disposed holes, which generate stream of calibrated cavitational bubbles, which enter the stream slotted zone with the purpose of decomposition of cavitational bubbles and creation of their secondary stream.
  • the operating fluid accelerator-promoter is additionally equipped with a slotted ejector ( 23 ) and with a chamber of the operating stream increased pressure ( 1 ), which possesses a slotted ejection accelerating passage disposed tangentially to the pass of the central manifold ( 2 ) of the heat-generator ( FIG. 1 ).
  • the central manifold ( 2 ) of the heat-generator is connected to its central part ( 7 ) which comprises a static cavitator ( 3 ) with radially disposed holes ( 4 ) generating a stream of calibrated cavitational bubbles, and possesses radial passages ( 5 ) in the slotted stream zone.
  • the static cavitator ( 3 ) also comprises a cavitating Laval nozzle ( 6 ), that provides instantaneous narrowing and widening of the main fluid stream and conducts the formation of a secondary stream of decomposed cavitational bubbles.
  • the continuously working cavitational heat-generator additionally comprises separating flanges ( 10 , 11 ) of the main fluid stream with a conical splitter, which under pressure uniformly distributes the operating fluid through slotted tangentially directed passages ( 12 , 23 ) into the outlet fitting passages ( 14 ) of the heat-generator, disposed concentrically against the central manifold ( 2 ) of the heat-generator, which are at least five, and a feeding pipe ( 21 ) of the heating system, or hot water delivery to consumers.
  • the outlet fittings ( 14 ) are equipped with static cavitators ( 15 ) with radially disposed holes ( 16 ), which generate stream of calibrated cavitational bubbles, annular channels ( 17 ) in the fitting body ( 19 ) and cavitating Laval nozzles ( 18 ), which decompose cavitational bubbles.
  • the outlet fittings ( 19 ) are additionally equipped with nozzle outlets ( 20 ) of the heat-generator, their angle of inclination being 45° to the fitting axis and directed sideways from the central manifold ( 2 ) of the heat-generator.
  • FIG. 9 a schematic sketch of the continuous cavitation heat-generator and its units is presented, and also a diagram ( FIG. 9 ), which illustrating realization of the claimed method in accordance with the invention.
  • the pump ( 35 ) After filling the tank with the operating fluid ( 36 ) in the amount necessary, as it has been mentioned before, with its initial temperature above 5° C., the pump ( 35 ) is turned on without participation of the control-regulating device assemblage ( 49 ), and the heating operational fluid occurs by the instrumentality of the heat-generator up to the temperature of 90° C., a thermocouple ( 40 ) controlling the heating process.
  • a manual control valve ( 42 ) smoothly opens and the operating fluid enters the heating circuit with heat exchangers ( 44 ) the heat-generator being turned on, and at the same time the faucets ( 48 , 51 ) are to be opened.
  • thermocouple ( 46 ) takes readings of the heat-generator in the return pipe ( 45 ). After filling the heating system with the operating fluid, the valves ( 42 , 48 , 51 ) are got closed, the pump is turned off and the heat carrier operating temperature is displayed on the control-regulating devices in the feeding and the return pipes of the heating system. The upper temperature of closing of the electrohydrovalve ( 41 ) is set, it being lower than the operating fluid temperature of 90° C.
  • the temperature of the opening of the electrohydrovalve ( 47 ) is set, for example, 60° C., and that of the automatic turning on of the pump ( 35 ) for starting heat-generator operation.
  • the temperature of 90° C. is also set for the opening of the electrohydrovalve ( 41 ). After this, the pump and the heat-generator start automatically.
  • the valves gets opened ( 41 ) and ( 47 ) and the heat-generator pressurizes water into the system, and at the same time, it continues to heat the operating fluid in the tank.
  • valves ( 41 , 47 ) close automatically, the pump is turned off until the cooling of the system levels 60° C., whereupon the valve ( 47 ) is opened and the pump automatically starts and the heat-generator starts, which delivers water into the system through the open valve. ( 41 ) after its proper heating.
  • the time necessary to level the temperature of the heating required will be petty, due to the fact that the water mass entering at the temperature of 60° C.
  • the fluid (water) stream by the instrumentality of the pump ( 35 ) enters the manifold pass ( 32 ) of the accelerator-promoter ( FIG. 2 ) at the velocity of 7 m/sec, then it goes to the conical part of the static cavitator ( 31 ), where it is swirled and gains the velocity of 9 m/sec. At such velocity, the fluid stream enters the inner passage of the static cavitator ( 31 ) its diameter being 2.4 times less than the manifold pass ( 32 ), and at the same time the fluid stream velocity increases up to 14 m/sec.
  • the inner passage of the static cavitator is no-go, consequently, reaching its conical end, the main stream is additionally swirled and gets return motion, and at the same time due to the turbulization and heat generation due to the transformation of the stream kinetic energy into heat energy, the primary process of cavitational bubbles origination occurs.
  • the main stream abruptly changes its motion direction, and at the same time heat energy is released additionally entering the stream slotted zone at the velocity of 24 m/sec and goes to the manifold radial passages ( 30 ), where the active process of cavitational bubbles collapse occurs with the energy release and local increase of the cumulative streams velocity up to 700 m/sec, and also primary bubbles decomposition in their saturated stream with lesser diameter up to 20-25 ⁇ 10 ⁇ 6 m.
  • Air-to-water mass of beads originates, which is compressible (as opposed to fluid), with the volume air contents of 0.8 that results in originating of additional shock waves and supersonic flow.
  • Sonic speed for the air-to-water mass is figured in accordance with the Wood formula: a ⁇ P ⁇ ⁇ ( 1 - ⁇ ) ⁇ p f where:
  • the main fluid stream enters the manifold conical passage ( 28 ), where its velocity again increases up to 5 m/sec and in the manifold cylindrical pass ( 28 ) of the diameter equaling 0.5 of that of the manifold pass ( 32 ), where its velocity increases up to 9 m/sec and an abrupt stream motion direction change occurs due to the guiding conical slant of the flange ( 27 ) in the ejection accelerating passage ( 29 ), which is disposed tangentially to the manifold pass ( 26 ), and at the same time the main fluid stream velocity increases up to 14 m/sec.
  • the stream is swirled and this results in the heat energy release.
  • the main fluid stream enters the manifold conical passage ( 25 ), where it again acquires the velocity of 9 m/sec and enters the inner passage of the static cavitator ( 24 ), where the same physical phenomena occur, as when the stream passing the static cavitator ( 31 ) with heat energy release.
  • the flange of the stream motion direction change and passages ( 25 , 26 ) and the static cavitator ( 24 ) of the manifold ( 22 ), successive increasing of the main fluid stream temperature occurs.
  • a slotted ejector ( 23 ) with holes is installed, when passing through them, the main stream acquires acceleration and cavitational bubbles are being formed, which collapse in the higher pressure chamber ( 1 ) and heat energy is released.
  • the slotted ejection acceleration passage disposed tangentially to the manifold pass ( 2 )
  • the main fluid stream enters the pass ( 2 ) of the heat-generator central manifold at the velocity of 9 m/sec, then it is swirled and heat energy is released.
  • the fluid stream which is swirled in the outlet fittings ( 14 ), will be influenced by Coriolis force, which will divert the external fluid layers in the direction perpendicular to its relative velocity and exert pressure upon the manifold pass walls ( 14 ), which will result in heat energy release.
  • the slotted passage cross-section area ( 13 ) depends on the heat carrier volume, which is to be delivered to the feeding pipe ( 21 ) and is a variable quantity, due to which it regulates the heat carrier delivery rate.
  • the fluid stream enters the inner running passages of the static cavitators ( 15 ), passes through the radial passages ( 16 ), the slotted stream zone with annular channels ( 17 ) in the manifold body ( 19 ) and cavitational Laval nozzles ( 18 ), and at the same time the same physical processes and heat energy release occur, as when passing the fluid stream through the accelerator-promoter of static cavitators ( FIG. 2 ) and the heat-generator central manifold ( 2 ).
  • the cavitational generator produces large amount of heat energy for heating considerable volume of fluid and continuity of its action with simultaneous delivery of the fluid to the feeding pipe.
  • the continuously working cavitational heat-generator and the claimed method of getting heat in accordance with this invention, can be used for autonomous heating of buildings and different purposes constructions, in agriculture, in technological operating processes or for energy generating.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Thermal Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Steam Or Hot-Water Central Heating Systems (AREA)
  • Jet Pumps And Other Pumps (AREA)
  • Physical Water Treatments (AREA)
  • Exposure And Positioning Against Photoresist Photosensitive Materials (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Sorption Type Refrigeration Machines (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US10/584,796 2003-12-31 2004-03-31 Method for producing heat for heating building and constructions and a continuous cavitation heat generator Abandoned US20070152077A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
UA20031213218A UA66334C2 (ru) 2003-12-31 2003-12-31 Способ получения тепла для отопления зданий и сооружений и кавитационный теплогенератор непрерывного действия
UA20031213218 2003-12-31
PCT/UA2004/000019 WO2005064244A1 (fr) 2003-12-31 2004-03-31 Procede pour produire de la chaleur et chauffer des immeubles et constructions ainsi que generateur de chaleur par cavitation a action ininterrompue

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US20070152077A1 true US20070152077A1 (en) 2007-07-05

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US10/584,796 Abandoned US20070152077A1 (en) 2003-12-31 2004-03-31 Method for producing heat for heating building and constructions and a continuous cavitation heat generator

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US (1) US20070152077A1 (ru)
EP (1) EP1706679B1 (ru)
CN (1) CN1918440B (ru)
AT (1) ATE416350T1 (ru)
CA (1) CA2554673A1 (ru)
DE (1) DE502004008603D1 (ru)
EA (1) EA008132B1 (ru)
PL (1) PL1706679T3 (ru)
UA (1) UA66334C2 (ru)
WO (1) WO2005064244A1 (ru)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013102247A1 (pt) * 2012-01-02 2013-07-11 Ioel Dotte Echart Rubem Gerador de cavitação hidrodinâmica e hidrossônica
RU2490556C2 (ru) * 2011-04-05 2013-08-20 Александр Семенович Фролов Теплогенератор устройства для отопления помещений

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006006161A1 (de) * 2006-02-10 2007-08-16 Juri Steinhauer Kavitationserzeuger
KR100802475B1 (ko) * 2007-03-08 2008-02-12 (주) 볼텍스웨어 캐비테이션을 이용한 고온발생 방법 및 그 장치
WO2018030967A1 (en) * 2016-08-09 2018-02-15 Sabanci Üniversitesi An energy harvesting device

Citations (6)

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Publication number Priority date Publication date Assignee Title
US3721521A (en) * 1971-04-30 1973-03-20 Us Army Apparatus for converting pressure energy to thermal energy
US3961485A (en) * 1973-11-06 1976-06-08 Michael Eskeli Turbine with heat intensifier
US4344567A (en) * 1980-12-31 1982-08-17 Horne C James Hydraulic heating system
US4364239A (en) * 1980-06-20 1982-12-21 Electricite De France (Service National) Hot water supply apparatus comprising a thermodynamic circuit
US4372254A (en) * 1981-01-23 1983-02-08 Edmund Hildebrandt Hydraulic heat generator
US6493507B2 (en) * 1997-01-30 2002-12-10 Ival O. Salyer Water heating unit with integral thermal energy storage

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RU2045715C1 (ru) * 1993-04-26 1995-10-10 Юрий Семенович Потапов Теплогенератор и устройство для нагрева жидкостей
UA7205A (ru) 1994-09-15 1995-06-30 Юрій Семенович Потапов Устройство для нагревания жидкости и теплогенератор, который используется в нем
RU2142604C1 (ru) * 1998-01-26 1999-12-10 Петраков Александр Дмитриевич Способ получения энергии и резонансный насос-теплогенератор
RU2160417C2 (ru) * 1998-05-29 2000-12-10 Петраков Александр Дмитриевич Насос-теплогенератор
UA47535C2 (ru) 2000-05-18 2002-07-15 Леонід Павлович Фоминський Способ получения тепла
RU2165054C1 (ru) * 2000-06-16 2001-04-10 Юрий Семенович Потапов Способ получения тепла
AT410591B (de) * 2001-10-04 2003-06-25 Newtech Innovations & Technolo Wärmegenerator

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3721521A (en) * 1971-04-30 1973-03-20 Us Army Apparatus for converting pressure energy to thermal energy
US3961485A (en) * 1973-11-06 1976-06-08 Michael Eskeli Turbine with heat intensifier
US4364239A (en) * 1980-06-20 1982-12-21 Electricite De France (Service National) Hot water supply apparatus comprising a thermodynamic circuit
US4344567A (en) * 1980-12-31 1982-08-17 Horne C James Hydraulic heating system
US4372254A (en) * 1981-01-23 1983-02-08 Edmund Hildebrandt Hydraulic heat generator
US6493507B2 (en) * 1997-01-30 2002-12-10 Ival O. Salyer Water heating unit with integral thermal energy storage

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2490556C2 (ru) * 2011-04-05 2013-08-20 Александр Семенович Фролов Теплогенератор устройства для отопления помещений
WO2013102247A1 (pt) * 2012-01-02 2013-07-11 Ioel Dotte Echart Rubem Gerador de cavitação hidrodinâmica e hidrossônica

Also Published As

Publication number Publication date
EP1706679B1 (de) 2008-12-03
UA66334A (ru) 2004-04-15
PL1706679T3 (pl) 2009-07-31
WO2005064244A1 (fr) 2005-07-14
CN1918440A (zh) 2007-02-21
EA008132B1 (ru) 2007-04-27
ATE416350T1 (de) 2008-12-15
DE502004008603D1 (de) 2009-01-15
CA2554673A1 (en) 2005-07-14
UA66334C2 (ru) 2008-12-10
CN1918440B (zh) 2010-06-16
EA200601256A1 (ru) 2006-10-27
EP1706679A1 (en) 2006-10-04

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