WO2006004459A2 - Moteur hydraulique a gaz - Google Patents

Moteur hydraulique a gaz Download PDF

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Publication number
WO2006004459A2
WO2006004459A2 PCT/RU2005/000354 RU2005000354W WO2006004459A2 WO 2006004459 A2 WO2006004459 A2 WO 2006004459A2 RU 2005000354 W RU2005000354 W RU 2005000354W WO 2006004459 A2 WO2006004459 A2 WO 2006004459A2
Authority
WO
WIPO (PCT)
Prior art keywords
turbine
inter
turbine wheel
paragraph
engine according
Prior art date
Application number
PCT/RU2005/000354
Other languages
English (en)
Russian (ru)
Other versions
WO2006004459A3 (fr
Inventor
Vladimir Nikolaevich Kostioukov
Original Assignee
Kostioukov Vladimir Nikolaevic
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Kostioukov Vladimir Nikolaevic filed Critical Kostioukov Vladimir Nikolaevic
Priority to DE112005001521T priority Critical patent/DE112005001521T5/de
Publication of WO2006004459A2 publication Critical patent/WO2006004459A2/fr
Publication of WO2006004459A3 publication Critical patent/WO2006004459A3/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D1/00—Non-positive-displacement machines or engines, e.g. steam turbines
    • F01D1/02—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines
    • F01D1/06—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines traversed by the working-fluid substantially radially
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D1/00—Non-positive-displacement machines or engines, e.g. steam turbines
    • F01D1/32—Non-positive-displacement machines or engines, e.g. steam turbines with pressure velocity transformation exclusively in rotor, e.g. the rotor rotating under the influence of jets issuing from the rotor, e.g. Heron turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03B—MACHINES OR ENGINES FOR LIQUIDS
    • F03B1/00—Engines of impulse type, i.e. turbines with jets of high-velocity liquid impinging on blades or like rotors, e.g. Pelton wheels; Parts or details peculiar thereto
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C7/00—Rotary-piston machines or engines with fluid ring or the like
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/20—Hydro energy

Definitions

  • the invention relates to mechanical engineering and can be used in steam and gas turbine engines, in internal combustion engines.
  • the disadvantage of this design is the unreliability of the power mechanism.
  • the technical result achieved in this invention is to increase the reliability of the power mechanism, the expansion of application and simplified design.
  • the specified technical result is achieved in that the gas-hydraulic engine comprises a sealed housing in which a radial turbine, nozzle apparatus, a control system, fuel supply, cooling, control, etc.
  • the housing is cylindrical and mounted with a calibrated gap and possibility of rotation
  • a turbine wheel containing radial blades made between two side disks bent around the periphery in the direction opposite to the rotation of the turbine wheel, forming inter-blade channels with the possibility of periodic complete or partial discharge from the fluid filling them during rotation of the turbine wheel, from the side of the turbine shaft, holes are made in one or both side disks that enter from one side to the distributor, and from the other side into the inter-blade channels, from the outside at least one crescent-shaped guide vane filled with liquid adjoins the side of the cylindrical wall to the casing, each of which initially contains, along the rotation of the turbine wheel, an outlet formed from together with the hole in the cylindrical wall of the casing, then, in the direction of rotation of the turbine wheel, the crescent-shaped guide apparatus comprises a nozzle device formed together with a second, in the direction of rotation of the turbine wheel, hole in the cylindrical wall of the casing extending to the inter-blade channels of the turbine wheel, and
  • the outlet which contains a crescent-shaped guide apparatus, forms, together with the hole in the nilindrical wall of the housing, a channel in the form of a nozzle with a compressed section, the axis of which is directed towards the blades of the turbine wheel in the direction of rotation.
  • inter-blade channels of the turbine are made inclined to the radius.
  • inter-blade channels are made diagonally (inclined) to the turbine shaft.
  • the nozzle of the guide apparatus and the compressed section of the exhaust channel are made adjustable.
  • the inter-blade channels are made in the form of a jet nozzle, for example, tapering to the periphery.
  • the casing in the space on the side of the side disks of the turbine, is filled with working fluid.
  • the casing in space from the side of the turbine lateral disks remains empty, and the casing is provided with openings for pumping out fluid and gas flows through the gaps.
  • the balance of the working fluid in the guide apparatus and the inter-blade channels is maintained by various known methods, so that when the turbine rotates, the inter-blade channels that exit to the tap at the moment of contact with it are drained as much as possible from the working fluid and exit to the nozzle at the moment termination of contact with it is as filled as possible with working fluid.
  • the outlet of the first crescent-shaped guide vane is connected to the nozzle of the second turbine wheel of the crescent-shaped guide vane, in turn, the outlet of this guide vane is connected by a pipe to the nozzle of the previous one rotation of the turbine wheel of the crescent guide apparatus, with the outlet and nozzle of each individual crescent guide apparatus being separated by impermeable partitions.
  • inter-blade channels of the turbine in the part prior to the beginning of the bending of the blades, are cylindrical, and pistons with o-rings are mounted with the possibility of reciprocating movement from the center of the turbine to the periphery and back, and in the part after the bending of the blades, the inter-blade channels are filled liquid.
  • pistons mounted in the inter-blade channels of the turbine are made differential.
  • double action pistons are mounted in the inter-blade channels.
  • inter-blade channels are made radial-axial, in the radial part they are filled with liquid, and in the axial part pistons are mounted in them, for example, differential double-acting ones.
  • the engine contains a piston synchronization device, for example, one of the cavities of each double-acting piston at the moment of its movement to the shaft of the turbine wheel is filled with liquid and connected to the cavity of the other piston at the moment of its movement to the periphery, and the connecting pipelines of these cavities are connected to the additional motor kinematically connected to a pump.
  • a piston synchronization device for example, one of the cavities of each double-acting piston at the moment of its movement to the shaft of the turbine wheel is filled with liquid and connected to the cavity of the other piston at the moment of its movement to the periphery, and the connecting pipelines of these cavities are connected to the additional motor kinematically connected to a pump.
  • inter-blade channels in the part before the beginning of the bend of the blade the current is separated by a sealed flexible membrane, and after the beginning of the bending of the blades to the periphery of the turbine is filled with liquid.
  • the working fluid is a liquid with a high boiling point, for example mineral oil
  • the engine cooling system contains heat exchangers - steam generators, filled with a liquid with a low boiling point, for example water, and connected to an additional steam turbine.
  • FIG. 1 Gas-hydraulic engine in the form of a two-stroke wet-gas internal combustion engine. Side view, cut.
  • Figure 3. Gas-hydraulic engine with differential pistons of simple and double action. Front view, cut.
  • Figure 4. Gas-hydraulic engine as a two-stroke internal combustion engine with differential, double-acting axial pistons. Side view, cut.
  • Figure 5. Gas-hydraulic engine in the form of a steam or gas engine of triple action. Front view, cut.
  • the gas-hydraulic engine comprises a housing 1 in which the turbine wheel 2 is mounted rotatably with radial or radially inclined inter-blade channels 3 with blades 4 bent at the periphery opposite to the turbine rotation, with inlets 5 adjacent to the turbine wheel shaft side, for example , a mechanical distributor 6 mounted in the side cover of the housing 1, made in the cylindrical wall 7 of the housing 1, an opening in the form of an outlet 8 exiting into the crescent-shaped guide apparatus 9 is fixed outside the housing 1 and forming a nozzle apparatus 10 with the next hole after 8 in the cylindrical wall 7 of the housing 1 along the rotation of the turbine wheel 2, seals, for example, labyrinth 11 of the peripheral end of the turbine wheel 2, seals, for example, the front shaft 12 of the turbine wheel 2.
  • the gas-hydraulic engine operates as follows.
  • the inter-blade channel discharged from the working fluid is blocked by a cylindrical wall 7 of the housing 1 made behind the branch 8 along the rotation of the turbine wheel 2, then is aligned with the outlet 13, while the inlet 5 of the inter-blade channel 3 is aligned by means of a distributor 6 with the compressed air supply pipe, which enters the inter-blade channel 3 by purging it, at the end of the purge, through the end distributor 6 through the inlet 5 in the inter-blade channel 3, in gas and carburetor engines, fuel - air mixture can come.
  • the air compression cycle or the fuel-air mixture begins, in the case of air compression at the end of the compression cycle, for example, the hole 5 is aligned by means of a distributor 6 with a fuel nozzle through which to the inter-blade channel 3 fuel is injected and ignited by the temperature of the compressed air or from the spark plug (not shown) in the case of compression of the fuel-air mixture, hole 5 is aligned with the spark plugs at the end of the compression stroke ment and the fuel-air mixture is ignited.
  • the expanding combustion products expel the working fluid from the inter-blade channel 3, into the channel with compressed section 18 of the outlet 8, where the speed of the jet of the outgoing fluid increases, the reaction of the jet acts on the blades, forcing the turbine wheel 2 to rotate, which can also rotate thanks to the inter-blade channels 3 made along the periphery in the form of nozzles, for example, tapering.
  • the working fluid From the inter-blade channel 3 in the stroke of the working stroke, the working fluid enters the outlet 8, then, through the guide apparatus 9, enters the nozzle apparatus 10 and then to the blades 4 of the turbine wheel 2 where, due to a change in the direction of flow of the working fluid, it gives energy to the turbine wheel 2 forcing rotate it, while compressing the air or fuel located in this compartment - the air mixture in the compression stroke. Further, when the turbine wheel 2 rotates, the cycle repeats.
  • the liquid leaves it with high energy ejecting a liquid with low energy from the inter-blade channel ending the contact with the channel 18 of the outlet 8.
  • a gas-hydraulic engine as a four-stroke wet-gas engine works, for example, as follows.
  • the turbine wheel 2 rotates in the inter-blade channel 3 combined with the outlet 8
  • the liquid is discarded to the periphery and enters the guide apparatus 9, while the inlet 5 of this inter-blade channel is combined by means of a distributor 6 with the inlet a pipeline through which air or fuel-air mixture enters the inter-blade channel 3.
  • this inter-blade channel 3 is blocked by the cylindrical wall 7 of the housing 1, and then combined with the nozzle apparatus 10 by which the inter-blade channel 3 is filled with working fluid coming from the guide apparatus 9 in the compression stroke, then, when the turbine wheel 2 is rotated, the inter-blade channel 3 is blocked by a cylindrical wall 7 of the housing 1, while at the time of overlap, and also possibly earlier or later than this moment, the inlet openings 5 are combined with the distributor 6 Combined with spark plugs or shower nozzles, the fuel-air mixture ignites, while the inter-blade channel 3 is combined with a channel with a compressed section 18 of outlet 8.
  • the inter-blade channel 3 is blocked by part of the cylindrical wall 7 of the housing 1, and then is combined with the nozzle apparatus 10, through which the working fluid enters this inter-blade channel 3, forcing the piston 14 to move to the center of the turbine wheel2.
  • the air inside it is compressed in the combustion chamber 15, and air is pushed into the receiver from the supercharger stage 16.
  • the turbine wheel 2 rotates the inter-blade channel 3 is blocked by the wall 7 of the housing 1.
  • the inter-blade channel 3 is aligned with the channel with a compressed cross-section of the outlet 8, the expanding gases in the combustion chamber 15 push the piston 14 to the periphery of the turbine wheel 2, respectively, the working fluid is pushed into the outlet 8 and, due to the reaction of the liquid entering the outlet channel 8 or nozzle-shaped peripheral part of the inter-blade channel 3, gives energy to the turbine wheel 2, forcing it to rotate, while the air entering the supercharger 16 enters the receiver.
  • the inter-blade channel 3 of the turbine wheel 2 is blocked by a part of the cylindrical wall 7 of the housing 1, and then it is combined with the nozzle apparatus 10 and the piston 14 starts moving towards the center of the turbine wheel 2.
  • the combustion products by means of a distributor 6 (or another devices) rush to the second expansion stage 16 in other inter-blade channels 3, in which the piston 14 rushes in this case to the periphery of the turbine wheel 2, depending on the design of the gas-hydraulic engine, one or two cylinders simultaneously, whence, when the pistons 14 move in the opposite direction, the combustion products are discharged by means of a distributor 6 into the exhaust manifold or directly into the cavity of the housing 1 (if it is empty), and then into the exhaust manifold. Further, when the turbine wheel 2 rotates, the cycle repeats.
  • the low-pressure cavity 17 can be used to collect and remove outflows of gases and working fluid through the piston seals 14, and can be used as an additional step for the continued expansion of the combustion products.
  • the heat that is transferred to the working fluid during engine operation can be used, thanks to the heat exchangers, steam generators 19, in an additional steam turbine.
  • the air-fuel mixture located in the combustion chamber 15 is ignited, when the turbine wheel 2 rotates, the inter-blade channel 3 is combined with the channel with a compressed section 18 of the outlet 8 of the guiding apparatus 9, the differential piston 14 rushes to the periphery of the turbine wheel 2, pushing it out of the inter-blade channel 3 working fluid and, due to the reaction of the jet, causes the turbine wheel to rotate, while the air in the supercharger 16 is compressed and pushed into the receiver.
  • the combustion chamber 15 opens, for example, windows (not shown) made in the cylinder walls of the combustion chamber 15 and opening at the end of the movement of the piston 14 to the periphery turbine wheels 2 and combined, for example, with an exhaust receiver (not shown in the drawing), while the inlet 5 by means of a distributor 6 is combined with an air receiver (not shown shown) from which purge air enters the combustion chamber, expelling the residual combustion products, and filling the combustion chamber 15 with a fresh portion of air (at the end of the purge into the combustion chamber, for example, gaseous or atomized fuel can be supplied in gas or carburetor engines )
  • the inter-blade channels 3 are combined with the nozzle apparatus 10, while the energy of the working fluid entering the inter-blade channel 3 is activated by curved blades 4 due to the rotation of the jet and makes the piston 14 move to the center of
  • the combustion products come from the medium pressure stage 16, n the low pressure stage 17, in those inter-blade channels 3. whose pistons 14 move to the periphery of the turbine wheel 2, or the combustion products are pushed out, for example, by m of the distributor 6, in this case, the stage 17 is used to collect and remove the flow of gases and working fluid.
  • the turbine wheel 2 rotates, the cycle repeats.
  • a gas-hydraulic engine can be, for example, a motor compressor when, for example, the combustion chamber 15 is used as an internal combustion engine, causing the turbine wheel 2 to rotate, and the cavities of the middle 16 and possibly low pressure 17, differential piston 14 are used as the working bodies of the compressor or, e.g. pump
  • the gas-hydraulic engine works, for example, as one of the pressure stages, which work the energy of the expanding working fluid.
  • compressed gas or steam enters the inter-blade channel 3 through the distributor 6, where it expands, pushing the working fluid into the sickle-shaped guiding apparatus 9, forcing the turbine wheel 2 to rotate, and then the fluid from the nozzle 10 enters into the next inter-blade channel 3, releasing energy to the blades 4 and pumping the gas or steam in it into the distributor 6 and possibly into the hole 13, evaporating or carried away gas, the liquid is compensated by the supply of liquid, for example, through channels made in the area of the compressed section of the outlet channel 8.

Abstract

La présente invention relève de la mécanique, et peut être utilisée dans des moteurs à combustion interne, à vapeur et à turbines à gaz. Le moteur selon l'invention comprend un corps cylindrique, dans lequel est montée une roue de turbine rotative possédant des aubes radiales courbées sur leur périphérie dans le sens opposé au sens de rotation, qui sont périodiquement remplies de liquide lors de la rotation de la roue de turbine. Au moins un appareil de guidage en demi-lune est fixé sur le corps, ledit appareil de guidage formant tout d'abord une goulotte, puis, dans le sens de rotation de la roue de turbine, une buse, qui débouchent sur les canaux de la roue de turbine. La roue de turbine est dotée d'orifices, qui sont situés sur le côté de son axe et débouchent sur un distributeur possédant des systèmes d'alimentation en air, en gaz ou en vapeur, d'alimentation en carburant, d'allumage, etc. L'invention permet de simplifier la construction et d'améliorer la fiabilité, par exemple, de moteurs lents de grande taille et de turbines à vapeur et à gaz.
PCT/RU2005/000354 2004-06-28 2005-06-28 Moteur hydraulique a gaz WO2006004459A2 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112005001521T DE112005001521T5 (de) 2004-06-28 2005-06-28 Gashydraulikmotor

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
RU2004119638/06A RU2286462C2 (ru) 2004-06-28 2004-06-28 Газогидравлическая турбомашина
RU2004119638 2004-06-28

Publications (2)

Publication Number Publication Date
WO2006004459A2 true WO2006004459A2 (fr) 2006-01-12
WO2006004459A3 WO2006004459A3 (fr) 2006-03-09

Family

ID=35783256

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/RU2005/000354 WO2006004459A2 (fr) 2004-06-28 2005-06-28 Moteur hydraulique a gaz

Country Status (3)

Country Link
DE (1) DE112005001521T5 (fr)
RU (1) RU2286462C2 (fr)
WO (1) WO2006004459A2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012117374A (ja) * 2010-11-29 2012-06-21 Minaminihon Plant Sekkei Jimusho:Kk 反力タービン

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU186793U1 (ru) * 2018-10-17 2019-02-04 Сергей Александрович Зеленин Водокольцевой роторный вакуумный двигатель внешнего сгорания

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL31813C (fr) * 1930-08-17
DE356649C (de) * 1920-09-28 1922-07-27 Oskar Richter Gasturbine mit Hilfstreibfluessigkeit
SU69506A1 (ru) * 1946-05-03 1975-01-25 Коловратный двигатель внутреннего горени

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE356649C (de) * 1920-09-28 1922-07-27 Oskar Richter Gasturbine mit Hilfstreibfluessigkeit
NL31813C (fr) * 1930-08-17
SU69506A1 (ru) * 1946-05-03 1975-01-25 Коловратный двигатель внутреннего горени

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012117374A (ja) * 2010-11-29 2012-06-21 Minaminihon Plant Sekkei Jimusho:Kk 反力タービン

Also Published As

Publication number Publication date
DE112005001521T5 (de) 2007-05-10
RU2004119638A (ru) 2006-01-10
WO2006004459A3 (fr) 2006-03-09
RU2286462C2 (ru) 2006-10-27

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