US20050244268A1 - Self-regulating turbine - Google Patents

Self-regulating turbine Download PDF

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Publication number
US20050244268A1
US20050244268A1 US11/121,644 US12164405A US2005244268A1 US 20050244268 A1 US20050244268 A1 US 20050244268A1 US 12164405 A US12164405 A US 12164405A US 2005244268 A1 US2005244268 A1 US 2005244268A1
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US
United States
Prior art keywords
turbine
steam
gas
flow
vanes
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.)
Abandoned
Application number
US11/121,644
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English (en)
Inventor
Klaus-Peter Priebe
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
DEUTSCHE ENERGIE HOLDING GmbH
Original Assignee
Klaus-Peter Priebe
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 Klaus-Peter Priebe filed Critical Klaus-Peter Priebe
Publication of US20050244268A1 publication Critical patent/US20050244268A1/en
Assigned to DEUTSCHE ENERGIE HOLDING GMBH reassignment DEUTSCHE ENERGIE HOLDING GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: PRIEBE, KLAUS-PETER
Abandoned 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
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/02—Blade-carrying members, e.g. rotors
    • F01D5/04—Blade-carrying members, e.g. rotors for radial-flow machines or engines
    • F01D5/043—Blade-carrying members, e.g. rotors for radial-flow machines or engines of the axial inlet- radial outlet, or vice versa, type
    • F01D5/048—Form or construction
    • 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
    • F01D17/00—Regulating or controlling by varying flow
    • F01D17/10—Final actuators
    • F01D17/12—Final actuators arranged in stator parts
    • F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
    • 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
    • F01D17/00—Regulating or controlling by varying flow
    • F01D17/10—Final actuators
    • F01D17/12—Final actuators arranged in stator parts
    • F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
    • F01D17/146—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by throttling the volute inlet of radial machines or engines
    • 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
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/02—Blade-carrying members, e.g. rotors
    • F01D5/04—Blade-carrying members, e.g. rotors for radial-flow machines or engines
    • F01D5/043—Blade-carrying members, e.g. rotors for radial-flow machines or engines of the axial inlet- radial outlet, or vice versa, type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2270/00—Control
    • F05D2270/30—Control parameters, e.g. input parameters
    • F05D2270/304—Spool rotational speed

Definitions

  • the present invention relates to a self-regulating turbine.
  • variable guide vanes in particular, in order to alter the incoming flow angle and the incoming flow speed.
  • an inlet channel that does not have a constantly tapering, circular-invariant cross section, as in the case of exhaust turbochargers, for example, but instead a rectangular cross section, in which there is situated an elastic sealing band that is placed under tension and closes off the channel vertically.
  • an elastic sealing band that is placed under tension and closes off the channel vertically.
  • a second solution according to the invention is one in which the inlet channel is closed off by an adjustable-height, suitably shaped and spring-loaded lid, so that the channel cross section can likewise be adapted to the particular load condition.
  • a third solution according to the invention is to use an elastic material, suitable to the temperature and pressure range, to form the wall of an inlet channel; this expands as the pressure increases and thus forms a circular, constantly tapering cross section which is optimal at all times.
  • a comparable measure can be achieved at the turbine outlet by again having a co-rotating cylindrical body, in which the exit ends of the turbine vanes can be retracted such that the exit region can be largely closed off or fully opened up.
  • the co-rotating cylindrical body can have negative shapes on both sides to accommodate the particular turbine vanes, and a central bore in the middle for the fluid to flow through.
  • the co-rotating cylindrical body can be fashioned as an impeller, in which the guide channel is bladed.
  • the first and second measures mentioned above have the effect that the turbine, automatically adjusting to different load conditions, quickly reaches its rated speed even when the steam or gas mass flows are slight and the generator connected to the turbine likewise quickly reaches its rated voltage.
  • a limiting of the turbine speed is achieved in that the current flow through the generator is steered by a suitable, voltage-dependent control system and the increasing current flow presents a suitably high electromagnetic moment in opposition to the turbine torque.
  • the outer wall of the turbine outlet channel allows for heat to pass through Peltier elements to a cooling channel, where the working fluid of the secondary circuit flows before going to the heat exchanger. This measure makes possible a further recovery of current at the preferred temperature difference of 150° C. to 30° C.
  • the automatically adjusting turbine should preferably be used for current production with solar absorbers, but it can equally be used for other operating purposes with changeable loads. Given a suitable choice of material, an operation with hot gas from combustion processes is also possible.
  • the solar absorber at the upper end of the housing should be outfitted with a Peltier heat/current exchanger.
  • the warm side of the exchanger closes off the solar absorber housing at the inside.
  • the outer side of the exchanger is shaded and subjected to forced thermal ventilation and, thus, cooled.
  • a heat exchanger is provided downstream from the turbine-generator set, which cools the particular selected working fluid down to the absorber inlet temperature and furnishes the thermal energy recovered from the exchanger to a heating circuit or a heat reservoir, for example.
  • the working fluid can be a gas or a liquid that is evaporated in the absorber and condensed back in the heat exchanger coming after the turbine.
  • the desired direction of work of the working fluid is ensured by a check valve at the lower inlet of the working fluid into the solar absorber, which only allows a flow into the absorber from underneath.
  • the absorber tubes lying in or on the absorber surface can be filled with a good gas or steam-permeable and good heat-conducting filler material, such as copper wool, in order to achieve a better transfer of heat from the absorber surface through the wall surface of the absorber tube to the working fluid being heated.
  • the absorber tube can also be an extruded hollow profile with individual star-shaped sections, in order to present the largest possible heat transfer surface.
  • the inner pressure in the primary circuit should be coordinated with the flow temperature of the secondary circuit so that the working fluid in the primary circuit is exposed to a pressure whose corresponding boiling point is more than 5° C. above the flow temperature of the secondary circuit.
  • This variable inner pressure is accomplished by an automatic device in which the interior of the absorber tubes is connected to a pressure regulating body, which is connected to the working fluid of the secondary circuit via a membrane not permeable to gas or steam. At low flow temperatures, the membrane is stretched by a bimetallic spring and, thus, the pressure is reduced inside the evaporation device.
  • FIG. 1 is a graph showing efficiency of geometrically rigid turbines
  • FIG. 2 shows a first embodiment of a turbine with axial inlet flow and radial outlet flow
  • FIG. 3 shows the turbine embodiment of FIG. 2 with retractable turbine vanes
  • FIG. 4 shows an embodiment of a turbine with a radial inlet and outlet flow
  • FIG. 5 shows a configuration of the radial inlet channels
  • FIG. 6 shows blading of the inlet, middle, and outlet parts of an embodiment of the turbine
  • FIG. 7 is a system view of a coupled solar absorber with a turbine according to an embodiment of the invention.
  • FIGS. 8-12 depict an opened housing of a turbine and the rotor in different positions in respect to a counter-housing in which the rotor can be moved in to enlarge or to reduce the active area of the turbine blades;
  • FIG. 13 is a cross-sectional view of an embodiment of a turbine showing one type of construction for varying the active blades of the turbine rotor;
  • FIG. 14 shows an embodiment of the invention with the rotor moved to a position different from that shown in FIG. 13 ;
  • FIG. 15 shows a rotatable control cylinder
  • FIG. 16 shows an embodiment of the turbine with retractable turbine vanes moving against a spring action in accordance with another type of construction
  • FIG. 17 is a perspective exterior view of the embodiment of FIG. 13 .
  • a turbine is provided with an axial inlet flow and radial outlet flow according to an embodiment of the invention.
  • the turbine is designed for operation with varying gas or steam quantities at varying temperatures or pressures.
  • the flow gap is closed after reaching the rated speed in dependence on the available heated gas or steam quantity or the size of the flow gap between the turbine vanes and/or the turbine blade inclination and/or the length of the turbine vanes is automatically adjusted as a function of pressure and/or temperature and the change in current flow in the generator connected downstream from the turbine is used as an additional regulating quantity for limiting the speed of the turbine.
  • FIGS. 2 and 3 show a turbine in which several turbine sets 1 with an axial gas or steam borehole 2 are arranged axially to each other. Each turbine set 1 is arranged on a separating seating disk.
  • a control cylinder 3 loaded with a temperature and pressure-controlled spring force automatically opens up one, several, or all turbine sets depending on the gas or steam quantity.
  • one or more turbine stators 4 and turbine rotors 5 of a turbine set may be arranged intermeshing in a plane.
  • the available gap in the rotational plane is automatically regulated by a temperature and pressure-controlled spring force, depending on the quantity of gas or steam.
  • the turbine blade may be fastened from an elastic material so that, when gas or steam quantities are low, the tip of a turbine blade lies tangentially against the neighboring blade with only a small outlet gap. As the gas or steam quantity increases the turbine blade is spontaneously deformed so that a larger gap is opened up with a smaller angle of attack of the turbine blade.
  • the turbine outlet channel may be configured variably thanks to a temperature and/or pressure elastic leaf spring 26 , so that when gas or steam quantities are low only a slight outlet gap is opened up. When steam or gas quantities are larger, the leaf spring is simultaneously deformed so that a larger outlet gap is opened up in the turbine outlet channel.
  • FIG. 3 shows a turbine with retractable turbine vanes, including an impeller 6 with turbine vane holders, and a spring 9 for pretensioning a rotation body against impeller 6 .
  • the turbine inlet flow is radial, the turbine vane segments running from outside to inside between the turbine blades in a first segment of the channel can be retracted in a negative form co-rotating axially as an impeller 6 and change after a streamlined central flow channel of the impeller into a last segment in which the turbine blades running from inside to outside can again be retracted into the negative shape.
  • FIG. 4 shows a turbine with radial inlet and outlet flow including a turbine inlet rotation body 7 with turbine vanes, a turbine outlet rotation body 8 with turbine vanes, and a Peltier heat/current exchanger or Seebeck elements 14 at the turbine outlet channel.
  • a Peltier heat/current exchanger takes advantage of the Peltier effect in which current flow across a thermoelectric junction produces cooling or heating.
  • Seebeck elements take advantage of the Seebeck effect in which current will flow when two dissimilar conductors are made into a circuit so long as the junctions are at different temperatures. As shown in FIG.
  • the two rotation bodies 7 , 8 carrying the turbine vanes form, with the negative shape accommodating the turbine vanes in the shape of an impeller, a structural assembly that is pretensioned by one or more springs 9 so that when gas or steam flows are increasing the turbine vanes are partly or entirely opened up.
  • the inlet channel may be configured with a tapering profile and can be adapted, as a function of load, to the conditions of usage by an inlet channel variable height profile 10 shown in FIG. 4 or an inlet channel variable depth profile 11 shown in FIG. 5 .
  • This adaptation is achieved by springs 12 which are tensioned.
  • Tensioning springs 12 are shown in FIGS. 4 and 5 for the height or depth profile respectively.
  • FIG. 6 shows blading of the inlet, middle, and outlet parts of the turbine including a profile with a wall 13 .
  • the inlet channel which is configured with a tapering profile, may have a cross-sectional profile varying as a function of load.
  • Wall 13 of the profile may be made of a pressure-sensitive, elastic material.
  • the turbine and the generator may be connected downstream to a heat exchanger 16 which cools the working fluid of a first circuit and provides the heat recovered in this way to a second circuit.
  • the outer wall of the turbine outlet channel may have Seebeck elements 14 .
  • the outer side of the Seebeck exchanger is formed by a cooling channel 15 through which the working fluid of a secondary circuit flows before entering the heat exchanger 16 .
  • FIG. 7 shows a system view of a solar absorber coupled with a turbine having a downpipe 17 to an absorber inlet, a pressure regulating vessel 20 having a bimetallic controlled membrane 21 , and a Seebeck heat/current exchanger element 25 on the absorber.
  • the turbine with generator and the heat exchanger in the first circuit after downpipe 17 with a check valve or valves 18 closing it off, are followed by one or more absorber tubes 19 in an ascending absorber for incoming thermal energy, including solar energy, which supply hot gas or steam to the turbine.
  • An evaporable liquid or a gas may be used as the working fluid in the first circuit.
  • a working fluid which boils at low temperatures is used.
  • the pressure in the first circuit can be lowered to the suitable low boiling temperature with more than 5 degrees Kelvin above the flow temperature of the heat exchanger 16 by self-regulating vessel 20 with bimetallic membrane 21 .
  • the heater tubes for better transfer of heat to the working fluid, may be additionally outfitted with good heat-conducting and gas or steam-permeable filler bodies 22 .
  • the heater tubes may also be extruded profiles having individual flow channels separated by ridges.
  • Two or more absorbers may be alternately admitted to the turbine in pulsed mode or smoothed pulse mode across collective absorber tubes 23 .
  • the pulse operation is preferably regulated by coupled, pretensioned check valves 24 on the collective absorber tubes.
  • Either a rotating turbine base plate at the side away from the turbine vanes or the rotating impeller on its outside may have permanent magnets of alternating polarity.
  • the excitation windings of the generator may be arranged opposite the rotation gap.
  • the absorbers may be closed off by Seebeck elements at the upper end of the housing which are directly shaded and under forced air cooling from the outside.
  • FIGS. 8-12 show an opened housing of an embodiment of the turbine and the rotor in different positions in respect to a counter-housing in which the rotor can be moved in to enlarge or to reduce the active area of the turbine-blades.
  • FIG. 8 the blades are quite small as shown on the right hand side thereof.
  • the blades are larger in FIG. 9 and larger in FIG. 10 .
  • FIG. 11 is a side view of the turbine-blades with the blades being quite large.
  • FIG. 12 the blades just dive in the right hand side rotatable counter-part.
  • FIG. 13 shows turbine housing 30 in which a turbine wheel, i.e. turbine rotor 5 , is shifted against a spring 31 for movement deeper and deeper into a rotatable control cylinder 3 .
  • FIG. 15 shows control cylinder 3 in more detail and
  • FIG. 17 shows a tiny portion of control cylinder 3 .
  • Input channels and output channels are designated with reference numerals 32 and 33 in FIG. 13 .
  • a generator 34 is shown within housing 30 but may be outside housing 30 on the rotary shaft 35 of the turbine rotor 5 and the control cylinder 3 .
  • turbine rotor 5 In order to cause axial movement of turbine rotor 5 , turbine rotor 5 is fixed on a part of shaft 35 which is, for example, quadratic in its square area. See FIG. 13 .
  • FIGS. 13 and 17 there are at least two different types of constructions that can be used to vary the area of the active blades of the turbine.
  • One form of construction is shown in FIGS. 13 and 17 (and FIGS. 8-12 ) where the turbine rotor moves in and out of control cylinder 3 .
  • FIG. 16 Another possibility is shown in FIG. 16 where control cylinder 3 moves against a spring action and is shown also in FIG. 3 .
US11/121,644 2002-11-05 2005-05-04 Self-regulating turbine Abandoned US20050244268A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10251752A DE10251752C1 (de) 2002-11-05 2002-11-05 Selbstregelnde Turbine
DE10251752.5 2002-11-05
PCT/DE2003/003607 WO2004042198A2 (de) 2002-11-05 2003-10-30 Selbstregelnde turbine

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2003/003607 Continuation WO2004042198A2 (de) 2002-11-05 2003-10-30 Selbstregelnde turbine

Publications (1)

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US20050244268A1 true US20050244268A1 (en) 2005-11-03

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US11/121,644 Abandoned US20050244268A1 (en) 2002-11-05 2005-05-04 Self-regulating turbine

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US (1) US20050244268A1 (de)
EP (1) EP1563167B1 (de)
CN (1) CN100458105C (de)
AT (1) ATE400729T1 (de)
AU (1) AU2003291926A1 (de)
DE (3) DE10251752C1 (de)
ES (1) ES2307984T3 (de)
WO (1) WO2004042198A2 (de)

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Publication number Priority date Publication date Assignee Title
DE102007045993A1 (de) * 2007-09-26 2009-04-02 Continental Automotive Gmbh Laufradgehäuse mit einem variabel einstellbaren Strömungskanal
CN109505696B (zh) * 2019-01-16 2021-07-02 势加透博洁净动力如皋有限公司 一种自动调节式涡轮增压机

Citations (5)

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US2689528A (en) * 1950-01-25 1954-09-21 Armstrong Siddeley Motors Ltd Gaseous fluid turbine pump unit
US3073117A (en) * 1958-04-01 1963-01-15 Bendix Corp Axially movable turbine for varying the turbine inlet in response to speed
US3352536A (en) * 1952-06-11 1967-11-14 Nils T Almquist Self-regulating turbine
US4161371A (en) * 1949-11-16 1979-07-17 The United States Of America As Represented By The Secretary Of The Army Self-regulating turbine
US6367261B1 (en) * 2000-10-30 2002-04-09 Motorola, Inc. Thermoelectric power generator and method of generating thermoelectric power in a steam power cycle utilizing latent steam heat

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DE448685C (de) * 1925-11-10 1927-08-20 Karl Wernert Regelvorrichtung fuer die Saugseite von Kreiselpumpen, Verdichtern u. dgl.
US2442783A (en) * 1944-07-01 1948-06-08 Us Sec War Turbine rotor
DE866145C (de) * 1944-07-21 1953-02-09 Daimler Benz Ag Verfahren und Vorrichtung zum Anlassen von Zweikreis-Strahltriebwerken, insbesonderefuer Luftfahrzeuge
GB602706A (en) * 1945-11-09 1948-06-01 Albert Victor Gilbert Improvements in or relating to gas turbines
DE819094C (de) * 1949-05-26 1951-10-29 Karl Dr-Ing Roeder Turbinenstufe mit Duesenregelung und mindestens zwei Laufkraenzen
US2816731A (en) * 1955-10-07 1957-12-17 Gen Electric Turbine speed control
GB905663A (en) * 1959-06-01 1962-09-12 Havilland Engine Co Ltd Power plant including a gas turbine
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US3901474A (en) * 1973-12-27 1975-08-26 Taimei Kinzoku Kogyo Kabushiki Rotary valve
FR2285514A1 (fr) * 1974-09-23 1976-04-16 Belet Jean Yves Regulateur de pression d'echappement pour turbocompresseurs
NO150135C (no) * 1982-05-10 1984-08-22 Kongsberg Vapenfab As Anordning ved ramluftturbiner
DE4200507C2 (de) * 1992-01-11 1994-02-17 Armin Henry Kultscher Variable Strömungsmaschine
US5794431A (en) * 1993-07-14 1998-08-18 Hitachi, Ltd. Exhaust recirculation type combined plant
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Publication number Priority date Publication date Assignee Title
US4161371A (en) * 1949-11-16 1979-07-17 The United States Of America As Represented By The Secretary Of The Army Self-regulating turbine
US2689528A (en) * 1950-01-25 1954-09-21 Armstrong Siddeley Motors Ltd Gaseous fluid turbine pump unit
US3352536A (en) * 1952-06-11 1967-11-14 Nils T Almquist Self-regulating turbine
US3073117A (en) * 1958-04-01 1963-01-15 Bendix Corp Axially movable turbine for varying the turbine inlet in response to speed
US6367261B1 (en) * 2000-10-30 2002-04-09 Motorola, Inc. Thermoelectric power generator and method of generating thermoelectric power in a steam power cycle utilizing latent steam heat

Also Published As

Publication number Publication date
ES2307984T3 (es) 2008-12-01
DE10251752C1 (de) 2003-10-30
WO2004042198A3 (de) 2004-07-08
ATE400729T1 (de) 2008-07-15
AU2003291926A8 (en) 2004-06-07
CN100458105C (zh) 2009-02-04
WO2004042198A2 (de) 2004-05-21
DE10394044D2 (de) 2005-11-03
CN1708634A (zh) 2005-12-14
DE50310124D1 (de) 2008-08-21
EP1563167B1 (de) 2008-07-09
EP1563167A2 (de) 2005-08-17
AU2003291926A1 (en) 2004-06-07

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Owner name: DEUTSCHE ENERGIE HOLDING GMBH, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:PRIEBE, KLAUS-PETER;REEL/FRAME:020720/0113

Effective date: 20080318

STCB Information on status: application discontinuation

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