EP0432287A1 - Moteur rotatif - Google Patents

Moteur rotatif Download PDF

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Publication number
EP0432287A1
EP0432287A1 EP89122788A EP89122788A EP0432287A1 EP 0432287 A1 EP0432287 A1 EP 0432287A1 EP 89122788 A EP89122788 A EP 89122788A EP 89122788 A EP89122788 A EP 89122788A EP 0432287 A1 EP0432287 A1 EP 0432287A1
Authority
EP
European Patent Office
Prior art keywords
rotor
pressure
chamber
type rotary
displacement type
Prior art date
Legal status (The legal status 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 status listed.)
Granted
Application number
EP89122788A
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German (de)
English (en)
Other versions
EP0432287B1 (fr
Inventor
Waldemar H. Kurherr
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Individual
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Individual
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Filing date
Publication date
Priority to GB8926742A priority Critical patent/GB2238579B/en
Priority to AU45641/89A priority patent/AU642132B2/en
Application filed by Individual filed Critical Individual
Priority to AT89122788T priority patent/ATE129543T1/de
Priority to DE1989624647 priority patent/DE68924647T2/de
Priority to EP89122788A priority patent/EP0432287B1/fr
Publication of EP0432287A1 publication Critical patent/EP0432287A1/fr
Application granted granted Critical
Publication of EP0432287B1 publication Critical patent/EP0432287B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
    • F01C1/14—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F01C1/20—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with dissimilar tooth forms

Definitions

  • Another important aim of the instant invention is to show a continuous smooth torque power output at the power take-off shaft as necessary for high power energy conversion application.
  • Conventional steam turbines work at their maximum efficiency only at full load and a respective high rate of revolution. Under partial load condition the efficiency of conventional steam turbines deteriorates rapidly. It is therefore a further most important aim to show a rotary steam engine capable to work at all load conditions with an efficiency equal or even higher than at full load condition. It is furthermore the aim of the instant inventions to show a rotary steam engine capable to run with extreme wet steam, undegassed steam as well as steam containing large amounts of impurities.
  • the objects of the invention are attained by constructing a displacement-type rotary system steam-turbine engine that mainly functions as a displacing-type steam engine that in addition also partially utilizes the kinetic energy generated by the fast flowing steam molecules impinging upon the rotor blades thus functioning also similar to a radial flow turbine.
  • the instant invention comprises an upper half housing and a lower half housing whereby both half's are tightly screwed together with their flange rims.
  • the two-stage turbine without total internal pressure compensation consists preferably of three blades rotor chambers, six grooves rotor chambers and one gear chamber all situated parallel to each other on their respective shaft.
  • Each housing chamber is formed from preferably a set of three aligned and intersecting cylindrical first or second-stage chambers capable to embody one first or second-­stage blades rotor and two first or second-stage grooves rotors mounted on the left and right horizontally alongside the said blades rotor.
  • the gear chamber situated at the rear of the housing is up to a certain rotor diameter equipped with gear wheels having the same diameter as the rotors.
  • Rotors of very large diameter and high revolution are preferably equipped with five smaller gear wheels to keep the circumferential velocity of the gear wheels as low as possible.
  • the first-stage, and the two second-stage blades rotors as well as the large gear wheel are all mounted on the same shaft.
  • Each set of grooves rotors and the corresponding small gear wheel are also mounted on a mutual shaft.
  • Each set of blades rotor chambers and the corresponding small gear wheel are also mounted on a mutual shaft.
  • Each set of blades rotor chambers and the respective grooves rotor chambers are sealed from the other sets of chambers and from the gear chamber.
  • On the circumferential surface of the blades rotors and on the surface of the grooves rotors small gear-type teeth are arranged such that a contact-less meshing can be accomplished as said rotors rotate about their respective axis.
  • the large gear wheel and the small gear wheels are precision ground and mesh very exactly thus allowing the synchronization of the rotation of the contact-less meshing said rotors.
  • the housing further comprises for each chamber corresponding inlet ports and outlet ports situated diametrical to each other and leading to the respective blades rotor chamber.
  • Mounted longitudinally on the surface of the said blades rotors thick rotor blades are situated spaced radially equidistant from each other.
  • the grooves rotors possess a corresponding number of blade grooves varying in number respective to the number of rotor blades and the ratio of mutual rotor revolution.
  • Said gear-type teeth mesh contact-less but very tightly with the complementary teeth of the opposing rotor thus establishing a very effective dynamic friction-less labyrinth gear-­type sealing action between the meshing rotors thereby attaining a high volumetric efficiency.
  • the rotor blades of the said blades rotors and the said small gear-type teeth of the grooves rotors move as they rotate about their corresponding shaft very close to their respective hollow cylindrical interior chamber wall thus performing with their gear-type teeth a dynamic frictionless labyrinth sealing action thereby sealing that part of the cylindrical interior chamber that embodies the working medium under pressure from that part of the cylindrical interior chamber that embodies the working medium under pressure from that part of the cylindrical interior chamber that embodies the working medium in a state of partial expansion.
  • the sealing action subdivides the said cylindrical interior chamber parts into at least two different and sealed from each other pressure states.
  • the space volume displacing action of the pressurized medium within said chamber parts generates a continuous rotational work condition by continuously exerting a pressure upon that side of the rotor blades facing in the direction of rotation as said rotor blades pass tightly through their respective chamber.
  • the object of attaining a high volumetric efficiency is furthermore reached by utilizing the two sets of second stage chambers situated on each side of the set of the first-stage chamber as partial expansive working medium volume chambers.
  • the pressurized working medium introduced through the inlet ports of the first-stage chamber does work by forcing the said rotor blades in a displacing mode through the said first-stage chamber after which it expands into the interconnected two second-stage chambers.
  • the total chamber volume of the said two second-stage chambers is many times that of the former first-­stage chamber. Wherefore the ratio of the leakage rate of the pressure reduced working medium per chamber of the working medium is accordingly much lower. The energy inherent in the partially expanded lost working medium is subsequently much lower. Therefore, as the total volume of the second-stage chambers increase in relation to the first-stage chamber the energy loss through the leakage of the working medium comparatively decreases. Therefore the effective leakage of the working medium is reduced to a proportional fraction thus consequently resulting in a respective considerable additional increase of volumetric efficiency.
  • the erosion and corrosion within a steam turbine increases among other proportionally with the increase of the temperature of the working medium.
  • the flow velocity of the working medium exceeds only insignificantly the circumferential velocity of said blades rotors and consequently the erosion and corrosion effect is reduced respectively.
  • the rotor blades of the instant invention are designed very thick and short and therefore various types of surface coatings or special materials such as ceramics become applicable thus reducing the erosion and corrosion effects of the rotor blades even further.
  • a further reduction of erosion and corrosion is accomplished by constructing the blades rotor and the rotor blades hollow and thus perform with the aid of the coolant an internal cooling.
  • the pressure forces compensation of the blades rotor was achieved by arranging an even number of rotor blades on the blades rotor surface and by arranging the inlet ports, the outlet ports within the interior cylindrical chamber diametrical to each other such that the pressure force moments oppose and cancel each other.
  • To cancel the pressure force moments of the grooves rotors completely additional two pressure force compensation rotors are mounted between the first-­stage grooves rotors and the second-stage grooves rotors on their respective shaft.
  • the circumferential surface of the two said pressure forces compensation rotors is polished and a surface area equivalent in size times pressure and direction to counter all the opposing pressure force moments is sealed and connected by a tubing to a first-stage inlet port.
  • the pressure force compensation is thus performed automatically for all pressure states. Therefore, all axial forces, radial forces and even the forces exerted by the weight of the rotors can be compensated thus it becomes possible to run each pressure stage of this instant invention with a respective high steam pressure and revolution.
  • the instant invention as constructed reduces high pressure steam similar to a one or two stage radial flow tandem build turbine.
  • a speed control regulates the pressure and the volume of the working medium to be utilized for the displacing process.
  • the instant invention can also be used as a combination of a turbine and a pump or compressor.
  • the instant invention as illustrated in FIG. 1 and FIG. 3 comprises an upper half housing 1 and a lower half housing 2.
  • the said housing 1 and 2 embody sets of first and second stage chambers with their respective first and second stage rotors. Centrally situated are a large circular blades rotor chamber and one small circular grooves rotor chamber situated parallel at the left and one at the right side horizontally of the said large blades rotor chamber.
  • Both said housing half's are tightly screwed together with their polished flange rimes 7.
  • Both the upper and the lower said housing 1 and 2 embody an inlet port 3 and 5 and an outlet port 4 and 6 whereby the said ports are situated diametrically to each other.
  • To support the housing legs 8 and 9 are rigidly mounted to the lower half housing.
  • the first-stage blades rotor 12 is mounted on shaft 14 centrally within the housing. Parallel beside the said first-stage blades rotor 12 the grooves rotors 15 and 16 are mounted on their respective shaft 17 and 18. Mounted longitudinal on the surface of the said blades rotor 12 thick rotor blades 13 are situated spaced radially equidistant from each other.
  • the grooves rotors 15 and 16 possess a corresponding number of blade grooves 19 and 20 varying in number respective to the number of rotor blades 13 and the ratio of the mutual revolution.
  • the rotor blades 13 mesh with the blade grooves 19 and 20 contact-less.
  • the rotor blades 13 move contact-less very close to the adjustable preferably metal insert plates 10 and 11 thus sealing the inlet port 3 and 5 chamber sides from the outlet port 4 and 6 chamber sides wherefore through the introduction of a pressurized medium such as steam through the diametrically opposed inlet ports 3 and 5 a continuous rotational work condition is reached.
  • the said metal rotor chamber seal plates 10 and 11 are preferably to be of such materials that prevent seizure by a possible occurring contact with the rotor blades 13.
  • the side chamber seal plates 38 and 39 are made of such materials that seizure with the rotor blades 13 as well as the blades rotors and the grooves rotors be prevented.
  • the second-stage blades rotors 34 and 35 are mounted on the mutual central shaft 14 on each side of the said first-stage blades rotor 12 and the corresponding second-stage grooves rotors are mounted on shaft 17 and 18.
  • the total volume between two successive rotor blades of the blades rotors 34 and 35 are many times that of the volume of the blades rotor 12 thus permitting a respective second-stage internal steam expansion.
  • the pressure compensation rotors 25a, 25b, and 26a, 26b are mounted on the shaft 17 and 18 respectively.
  • FIG. 2 shows the pressure compensation rotors 25a and 25b mounted on their respective shaft 17 and 18.
  • the labyrinth seals 27, 28, 29 and 30 seal contact-less part of the polished surface of the pressure compensating rotors 25a and 25b from the chamber 50.
  • the inlet ports 3 and 5 are interconnected with the inlet ports 31 and 32 thus automatically producing an equal pressure exertion diametrically on the surfaces of the pressure compensating rotors 25a, 25b and 26a, 26b and the grooves rotors 15 and 16 whereby a total pressure compensation is attained. Contrary to the grooves rotors the blades rotors 12, 34 and 35 are always fully pressure compensated due to the fact that the steam pressure forces always occur diametrically wherefore the counter directed forces cancel each other.
  • outlet ports 4 and 6 of the chamber of the blades rotor 12 and outlet port 33 of the pressure compensating rotors are interconnected with the inlet ports of the chamber of the blades rotors 34 and 35 thus transforming leakage steam into additional working medium thereby improving the volumetric efficiency of the instant invention.
  • FIG.4 the two contact-less revolving rotor surfaces 51 and 52 without the gear-type teeth 21 and 22 have although with equal pitch circles 47 and 48 extreme large steam leakages through the gap 43a and 44a about the contact-­less meshing rotor blade 49 and the corresponding rotor groove 20.
  • the gap 43b and 44b shows with equal pitch circles 47 and 48 a far lesser steam leakage due to the sealing ability of the contact-­ less meshing gear-type teeth 21 and 22 thus producing a considerable increase in the volumetric efficiency.
  • the gap 43 and 44 prevents a steam pressure build-up as shown between the rotor blades 13 and 49 whereby otherwise an internal pressure compensation between said rotor blades would occur thus resulting in a periodic torque cancellation thus being perceptible as an uneven power output at the power take-off shaft.
  • the rotor blades are mounted within t-grooves 41 and possess at their tip grooves 42 to enhance their labyrinth sealing ability.
  • seizure preventive seal plates 38 and 39 are installed. Due to the pressure compensation of the rotors only minimal forces act on the rotor shafts 14, 17 and 18 thus permitting among other the application of fast turning ball bearings 45 and 46.
  • the seal 36 and 37 seal between all respective chambers.
  • the instant invention is used as a combination of turbine and pump or compressor by using the two blades rotors 34 and 35 to compress a medium such as air by using the inlet ports as outlet ports and the outlet ports as inlet ports for that medium and by furthermore using the blades rotor 12 to do work in a displacing fashion as described.
  • a medium such as air
  • the instant invention can be employed in various form such as compressor, pump, motor, etc..

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
EP89122788A 1989-11-27 1989-12-09 Moteur rotatif Expired - Lifetime EP0432287B1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
GB8926742A GB2238579B (en) 1989-11-27 1989-11-27 Displacement-type rotary system steam-turbine engine or compressor or pump.
AU45641/89A AU642132B2 (en) 1989-11-28 1989-11-28 Displacement-type rotary system steam-turbine engine
AT89122788T ATE129543T1 (de) 1989-12-09 1989-12-09 Rotationskolbenmaschine.
DE1989624647 DE68924647T2 (de) 1989-12-09 1989-12-09 Rotationskolbenmaschine.
EP89122788A EP0432287B1 (fr) 1989-11-28 1989-12-09 Moteur rotatif

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AU45641/89A AU642132B2 (en) 1989-11-28 1989-11-28 Displacement-type rotary system steam-turbine engine
EP89122788A EP0432287B1 (fr) 1989-11-28 1989-12-09 Moteur rotatif

Publications (2)

Publication Number Publication Date
EP0432287A1 true EP0432287A1 (fr) 1991-06-19
EP0432287B1 EP0432287B1 (fr) 1995-10-25

Family

ID=25627288

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89122788A Expired - Lifetime EP0432287B1 (fr) 1989-11-27 1989-12-09 Moteur rotatif

Country Status (2)

Country Link
EP (1) EP0432287B1 (fr)
AU (1) AU642132B2 (fr)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1995008698A1 (fr) * 1993-09-21 1995-03-30 Zhenyi Liao Rotors du type engrenant
WO1999046507A1 (fr) * 1998-03-11 1999-09-16 Osen Science & Technology Co., Ltd. Compresseur a gaz de type a dents complexes
DE102008010919A1 (de) 2008-02-25 2009-09-03 Markus Franssen Abfallverwertungsanlage zur Erzeugung von Energie
DE102009014410A1 (de) 2008-03-31 2009-10-01 Etag Production Gmbh Abfallverwertungsanlage zur Erzeugung von Energie
DE102009013632A1 (de) 2009-03-18 2010-09-23 Brück, Alexandra Verfahren und Vorrichtung zur Verstromung von Energieprodukten wie Gas und Treibstoffe
US8376369B2 (en) 2006-02-10 2013-02-19 Freudenberg-Nok General Partnership Seal with spiral grooves and contamination entrapment dams
US8454025B2 (en) 2010-02-24 2013-06-04 Freudenberg-Nok General Partnership Seal with spiral grooves and mid-lip band
US8919782B2 (en) 2012-10-19 2014-12-30 Freudenberg-Nok General Partnership Dynamic lay down lip seal with bidirectional pumping feature
US9297277B2 (en) 2011-09-30 2016-03-29 General Electric Company Power plant

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8925927B2 (en) 2006-02-10 2015-01-06 Freudenberg-Nok General Partnership Seal with controllable pump rate
US7494130B2 (en) 2006-02-13 2009-02-24 Freudenberg-Nok General Partnership Bi-directional pattern for dynamic seals
US7775528B2 (en) 2006-02-13 2010-08-17 Freudenberg-Nok General Partnership Bi-directional pattern for dynamic seals
US7891670B2 (en) 2008-02-01 2011-02-22 Freudenberg-Nok General Partnership Multi-directional shaft seal

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB843675A (en) * 1956-12-28 1960-08-10 Inst Francais Du Petrole Improvements in or relating to rotary compressors
US2956735A (en) * 1956-12-28 1960-10-18 Inst Francais Du Petrole Rotary compressor
DE2152517A1 (de) * 1970-10-22 1972-04-27 Przybylski Zdislaw Ryszard Rotationskolbenmaschine
DE2321639A1 (de) * 1973-04-28 1974-11-07 Georg Draeger Zahnradpumpe bzw. zahnradmotor
DE2330992A1 (de) * 1973-06-18 1975-01-02 Kernforschungsanlage Juelich Eine rotationskolbenmaschine mit axialsymmetrisch drehenden und beruehrungslos dichtenden kolben im kreisprozess eines heissluftmotors mit kontinuierlicher energiezufuhr
US3863610A (en) * 1972-08-18 1975-02-04 Raymond G Spinnett Rotary converters having specialized interleaving elements
FR2243607A5 (en) * 1973-09-10 1975-04-04 Widemann Antoine Rotary I.C. engine with gear type rotors - blades of central rotor engage recesses on adjacent rotors

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB843675A (en) * 1956-12-28 1960-08-10 Inst Francais Du Petrole Improvements in or relating to rotary compressors
US2956735A (en) * 1956-12-28 1960-10-18 Inst Francais Du Petrole Rotary compressor
DE2152517A1 (de) * 1970-10-22 1972-04-27 Przybylski Zdislaw Ryszard Rotationskolbenmaschine
US3863610A (en) * 1972-08-18 1975-02-04 Raymond G Spinnett Rotary converters having specialized interleaving elements
DE2321639A1 (de) * 1973-04-28 1974-11-07 Georg Draeger Zahnradpumpe bzw. zahnradmotor
DE2330992A1 (de) * 1973-06-18 1975-01-02 Kernforschungsanlage Juelich Eine rotationskolbenmaschine mit axialsymmetrisch drehenden und beruehrungslos dichtenden kolben im kreisprozess eines heissluftmotors mit kontinuierlicher energiezufuhr
FR2243607A5 (en) * 1973-09-10 1975-04-04 Widemann Antoine Rotary I.C. engine with gear type rotors - blades of central rotor engage recesses on adjacent rotors

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1995008698A1 (fr) * 1993-09-21 1995-03-30 Zhenyi Liao Rotors du type engrenant
US5682793A (en) * 1993-09-21 1997-11-04 Liao; Zhenyi Engaged rotor
WO1999046507A1 (fr) * 1998-03-11 1999-09-16 Osen Science & Technology Co., Ltd. Compresseur a gaz de type a dents complexes
US6352420B1 (en) 1998-03-11 2002-03-05 Osen Science & Technology Co., Ltd. Complex teeth-type gas compressor
US8376369B2 (en) 2006-02-10 2013-02-19 Freudenberg-Nok General Partnership Seal with spiral grooves and contamination entrapment dams
EP2110520A2 (fr) 2008-02-25 2009-10-21 Markus Franssen Installation de traitement des déchets pour la production d'énergie
DE102008010919A1 (de) 2008-02-25 2009-09-03 Markus Franssen Abfallverwertungsanlage zur Erzeugung von Energie
DE102009014410A1 (de) 2008-03-31 2009-10-01 Etag Production Gmbh Abfallverwertungsanlage zur Erzeugung von Energie
DE102009013632A1 (de) 2009-03-18 2010-09-23 Brück, Alexandra Verfahren und Vorrichtung zur Verstromung von Energieprodukten wie Gas und Treibstoffe
WO2010106130A2 (fr) 2009-03-18 2010-09-23 Brueck, Alexandra Procédé, dispositif et système de transformation d'énergie
US8454025B2 (en) 2010-02-24 2013-06-04 Freudenberg-Nok General Partnership Seal with spiral grooves and mid-lip band
US9297277B2 (en) 2011-09-30 2016-03-29 General Electric Company Power plant
US8919782B2 (en) 2012-10-19 2014-12-30 Freudenberg-Nok General Partnership Dynamic lay down lip seal with bidirectional pumping feature

Also Published As

Publication number Publication date
AU642132B2 (en) 1993-10-14
AU4564189A (en) 1991-06-06
EP0432287B1 (fr) 1995-10-25

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