EP0607357B1 - Verfahren, um eine turbine mittels eines strahlapparates anzutreiben - Google Patents

Verfahren, um eine turbine mittels eines strahlapparates anzutreiben Download PDF

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Publication number
EP0607357B1
EP0607357B1 EP92922988A EP92922988A EP0607357B1 EP 0607357 B1 EP0607357 B1 EP 0607357B1 EP 92922988 A EP92922988 A EP 92922988A EP 92922988 A EP92922988 A EP 92922988A EP 0607357 B1 EP0607357 B1 EP 0607357B1
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EP
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Prior art keywords
turbine
fluid
channel
rotation
speed
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EP92922988A
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English (en)
French (fr)
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EP0607357A1 (de
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Michèle MARTINEZ
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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
    • F01D17/00—Regulating or controlling by varying flow
    • 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
    • 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
    • F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
    • F01D15/06—Adaptations for driving, or combinations with, hand-held tools or the like control thereof
    • F01D15/062—Controlling means specially adapted therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F5/00—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
    • F04F5/44—Component parts, details, or accessories not provided for in, or of interest apart from, groups F04F5/02 - F04F5/42
    • F04F5/48—Control
    • 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
    • F05D2200/00—Mathematical features
    • F05D2200/10—Basic functions
    • F05D2200/11—Sum
    • 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
    • F05D2260/00—Function
    • F05D2260/60—Fluid transfer
    • F05D2260/601—Fluid transfer using an ejector or a jet pump
    • 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S415/00—Rotary kinetic fluid motors or pumps
    • Y10S415/904—Tool drive turbine, e.g. dental drill

Definitions

  • the present invention relates to a method for rotating a turbine and a corresponding turbine device.
  • Turbines have been known for a long time and are essentially constituted by a hub carrying blades, driven in rotation by a fluid (gas, liquid) passing through it.
  • driving a turbine with a fluid makes it possible to transfer the energy of the fluid to the axis of rotation of the turbine.
  • the rotation of this axis is used to drive an alternator to produce electric current, or to drive various tools (drilling, sawing ).
  • the devices described in these two documents include: an upstream fluid supply channel, a turbine, a downstream channel, means for injecting a primary fluid, means for admitting a secondary fluid and means for mixing the primary and secondary fluids.
  • the present invention aims to overcome all of these drawbacks and in particular to create a turbine whose nominal operating point is not associated with a transonic flow speed, in order to avoid all the problems linked to the disturbances induced by such flow.
  • an operating point is characterized by a value torque (rotation speed, power) or (rotation speed, torque).
  • torque rotation speed, power
  • rotation speed, torque rotation speed, torque
  • a nominal operating point is an operating point corresponding to a maximum power.
  • the operating point corresponding to maximum torque will be called the operating point at nominal torque.
  • One of the aims of the invention is to obtain powers comparable to those obtained on conventional turbines, but with flow velocities compatible with undisturbed or little disturbed flows.
  • the Venturi effect transforms the energy of the primary fluid injected by a nozzle with low mass flow and high speed and pressure, into the energy of a fluid (resulting from the mixing of said primary fluid with the secondary fluid sucked in by Venturi effect) characterized by a high mass flow and a low flow speed.
  • This force F is obtained by producing a high mass flow Dmm equal to the sum of the mass flows dmp + Dms, while having fluid flow speeds We and Ws sufficiently low to be compatible with a flow that is not very disturbed.
  • the method according to the invention makes it possible, by acting continuously on the pressure and / or the speed of the primary fluid and / or on any other dimensional or functional parameter of the turbine device, to be able to adapt the nominal operating point of the device at setpoint operating point.
  • the actual speed is measured continuously and then compared to a set speed.
  • This setpoint speed is determined for a given application. For example, if the turbine drives a milling tool, this speed can be 36,000 rpm.
  • one or more dimensional or functional parameters are continuously modified so that the measured speed of rotation is equal to the reference speed of rotation.
  • the inlet sections of the secondary fluid, injection of the primary fluid and outlet of the fluid ejection channel are continuously modified so as to equal, as much as possible, the setpoint operating point and nominal operating point.
  • the injection of the primary fluid in addition to the variation in pressure of the primary fluid, can be done according to a helical trajectory inducing self-limitation and self-adaptation of the operating regime of the turbine.
  • Such an injection mode is said to be helical.
  • the injection of the primary fluid takes place in zones close to the walls of said supply channel.
  • Such an injection mode is said to be parietal.
  • the device according to the invention is provided with actuators adapted to vary the intake section of the primary and secondary fluids, as well as the section of the ejection channel. It is thus possible to modify the nominal operating point of the turbine at will and to adapt it continuously to the set operating point.
  • the aim of the present invention is to drive a turbine in rotation, with a relatively low speed of rotation ⁇ , of the order of 0 to 60,000 rpm, but with a high torque C.
  • the product C. ⁇ which gives the power P of the turbine remains high, without however the speed of rotation ⁇ being.
  • a modification is made to the dimensional parameters of the turbine device (variation of the inlet section of the secondary fluid, of the section of injection of the primary fluid and of the section of ejection of the ejection channel).
  • the nominal operating point of the turbine is modified and the actual rotation speed is continuously regulated so that it corresponds to the set rotation speed.
  • the injection means 14 (FIG. 1) of primary fluid Fp into the supply channel 11 is placed at the upstream part 11a of the supply channel 11.
  • This means 14 includes a nozzle 15.
  • a secondary fluid Fs is sucked into the upstream supply channel by the depression created by the injection of the primary fluid. Once in the upstream supply channel, these two fluids mix in the downstream part 11b of the supply channel 11. The length of this supply channel partly conditions the characteristics of the mixture of the fluids.
  • a converging channel 16 is placed upstream of the turbine 12 and is intended to accelerate the mixing of fluids.
  • a deflector means 17, called the upstream distributor, constituted by a fixed turbine wheel is placed upstream of the turbine 12, in order to direct the mixture of fluids optimally on blades 18 of the turbine 12.
  • the turbine 12 is thus driven in rotation.
  • the mixture of fluids is then ejected through the ejection channel 13 outside the turbine device.
  • the purpose of such a channel is to adapt in particular the pressure of the fluid leaving the turbine to that of the fluid present around the ejection section.
  • the rotation of the turbine is used for any application, for example for driving tools, etc. as will be detailed with reference to FIG. 3.
  • the device according to the invention is continuously regulated by the control and regulation assembly 50.
  • the converging channel 16 can be integrated into the upstream distributor 17.
  • the injection means 14 can take different forms.
  • Figures 3 and 4 show a first variant of the device according to the invention.
  • the injection means 114 consist of two pipes 130 opening into the side wall of the upstream supply channel 111.
  • these pipes are inclined at an angle ⁇ (FIG. 3) determined relative to the axis A of the device, and an angle ⁇ (FIG. 4) between the axis of the pipe 130 and a diametrical plane F passing through the axis of the turbine and the center of the injection section at the wall of the channel 111.
  • the primary fluid Fp drives the secondary fluid Fs in a helical trajectory (helical injection) along the walls (parietal injection) of the upstream supply channel 111.
  • This type of injection is called parieto-helical injection.
  • This injection mode has the advantage of being self-adapting.
  • the mass flow Dms of the secondary fluid also increases.
  • the speed of the secondary fluid in the injection plane of the primary fluid in the supply channel has a module which increases and a direction which tends to approach the axis of the turbine.
  • the flow of the mixture has a general incidence which decreases in the inlet plane of the turbine. Therefore, the available power tends to decrease if the increase in secondary mass flow is not taken into account and vice versa if the speed of rotation of the turbine decreases.
  • the speed of rotation corresponding to such a power peak is 12,000 rpm for a turbine with a diameter of 30 mm and a supply of primary fluid of the parieto helical type with three equally distributed inlet channels. along the circumference of the inlet channel (the angles ⁇ and ⁇ of inclination of the inlet pipes being 45 °).
  • the number of pipes 130 for injecting primary fluid may vary.
  • the ejection channel 113 has an axial direction. It will also be noted that with such an injection mode (helical parieto), it is not necessary to place a deflector device upstream of the turbine 112.
  • the axis of rotation of the turbine can be directly constituted by a mandrel rod 160 of a tool 180.
  • the turbine 112 is force-fitted onto the rear part 160 (mandrel rod) of the cylindrical tool 180, which can be a cutter.
  • the tool may have, for this purpose, at its mandrel rod, a set of small rectilinear edges oriented along the axis of rotation of said tool.
  • the tool can be associated with an intermediate fixing part (not shown).
  • the suspension bearing of the tool-turbine assembly is constituted by the bearings 183 and 184.
  • the bearing 183 abuts on the hub of the turbine.
  • a spacer 185 mounted just sliding on said tool, maintains the spacing with the bearing 184 so as to ensure the necessary functional clearance along the axis of rotation at the level of the bearing body 186.
  • a ring 187 made of a material whose coefficient of thermal expansion is lower than that of the material constituting said tool is mounted tight on said tool and comes to immobilize in translation (along the axis of rotation of the tool) the bearings 183 and 184 and the spacer 185.
  • the assembly thus produced consists of a small number of simple, inexpensive and low inertia parts around the axis of rotation.
  • the mode of injection of the primary fluid is still different.
  • the injection means 214 here consists of four conduits 230 (three are shown) opening out inside the supply channel 211, so that the primary fluid Fp is injected parallel to the axis A of the device and the along the walls. Such an injection mode is said to be parietal.
  • the primary fluid drives the secondary fluid to the turbine.
  • the number of pipes 230 for introducing the primary fluid may vary and that, preferably, the plurality of pipes is distributed along the circumference of the supply channel 211.
  • each pipe 230 can pivot around its horizontal axis, to generate a flow that is no longer axial but helical.
  • a helico-parietal flow is obtained with the advantages cited with reference to FIGS. 3 and 4, and associated with an upstream distributor 217.
  • Figures 6 and 7 show a third alternative embodiment of the turbine device according to the invention. As before, the references of FIG. 2 are repeated increased by three units of a hundred for the equivalent means represented in FIGS. 2 and 6.
  • the secondary fluid is introduced into the supply channel by an inlet device 350 having an opening 351 with variable section.
  • the input device is screwed and unscrewed on the body of the supply channel 311 by means of a thread 352.
  • This screwing (or unscrewing) is controlled by a means for modifying the input section, namely the actuator 353.
  • This actuator 353 is itself controlled by the processing means 321. As shown by arrow B, l action of this actuator 353 makes it possible to vary the inlet section of the secondary fluid.
  • an actuator 354 for varying the ejection section of the device allows the screwing or unscrewing of an output device 356 via a thread 357. As shown by arrow C, the action of this actuator 354 makes it possible to vary the ejection section.
  • the actuator 354 is controlled by the processing means 321.
  • An actuator 355 making it possible to vary the section for injecting the primary fluid into the supply channel 311 is also provided.
  • the primary fluid Fp is introduced into the supply channel 311 passing through a minimum section 358 called the neck section of the flow, this section varying through the actuator 355.
  • This neck is created (FIG. 7), on the one hand, by an annular bulge 359 of the wall of the supply channel 311 and, on the other hand, by a displaceable element 360 placed in the upstream part 311a of the channel. brought 311 and opposite the annular bulge 359.
  • the introduction of the primary fluid Fp into the supply channel 311 takes place parallel to the longitudinal axis A of the device. This injection is carried out around the entire circumference of the inlet channel and near the walls. This injection is called parieto-annular injection.
  • annular diverging convergent nozzle As shown in FIG. 7, the respective shapes of the body 370 of the supply channel 311 and of the displaceable element 360 which faces it constitute an annular diverging convergent nozzle.
  • Said annular diverging convergent nozzle supplied with primary fluid by an annular section 371, therefore has a neck 358 and an outlet section 372 whose respective surfaces can vary when the actuator 355 drives the element 360 in translation.
  • the primary fluid undergoes subsonic acceleration until reaching the sonic speed at said neck 358.
  • the primary fluid In the divergent part of said nozzle, the primary fluid undergoes supersonic acceleration.
  • the primary fluid supply pressure must be sufficient so that, taking into account the value of the surface of the injection section 372, the ejection of said primary fluid into the supply channel is supersonic and at a static pressure higher than that of said secondary fluid in section 373 of element 360. Indeed, it then creates on the outlet lips 374 of element 360 an expansion beam and a turbulent wake capable of promoting the exchange of energy between said primary and secondary fluids.
  • the parietal injection following a convergent / divergent annular nozzle makes it possible, on the one hand, to increase the energy exchange surface between said primary and secondary fluids and, on the other hand, to obtain in the plane d input 375 (FIG. 6) of said distributor 317 has an optimum speed profile characterized in that the local average speed is all the more important as it is located near the head of the blades 318 of said distributor 317.
  • Such a dimensional and functional arrangement of a convergent / divergent nozzle at the level of the injection of the primary fluid can be generalized to all the injections of primary fluid, whatever the variant considered.
  • Such a device makes it possible, by acting on the dimensions of the primary and secondary fluid intake channels and on the dimension of the ejection channel, to vary the nominal operating point of the turbine.
  • Another variant of the ejection device consists in producing a duct ejection channel leading the fluid from the outlet plane of the turbine to the level of the intake of the secondary fluid and thus making it possible to recycle in the device itself a part of the ejected fluid.
  • the turbine 12 (FIG. 8) is constituted by a cylindrical hub on which blades 18 which are circularly distributed are disposed radially. These blades are identical for the same turbine.
  • the leading edge angles are constant along the leading edge for all the blades of the same turbine, the same for the trailing edge angles.
  • the profile chord is constant for all the profiles of all the blades of the same turbine.
  • the thickness of a profile is constant, except in the immediate vicinity of the trailing edge and the leading edge.
  • the thickness of the profiles of a blade increases from head to foot of the blade in order to take into account the increasing mechanical stresses from head to foot of the blade.
  • the blades have a constant chord, a constant thickness along a cylindrical section having as axis that of said turbine, constant leading edge angles, constant trailing edge angles, curved surfaces of intrado and upper surface generated by a conical surface whose apex is the point of intersection of the axis of said turbine with the planes, perpendicular to the axis of said turbine, of inlet for the upstream part and outlet for the downstream part, and the apex angle of which is a function of the leading edge angle for the upstream part and the trailing edge angle for the downstream part.
  • Such blades are simple to produce (machining, molding, etc.) and inexpensive.
  • such blades have the advantage, when the speed of the turbine increases, of also increasing the speed of the flow in the inter-blade channel. From a certain value of said flow speed, expansion and recompression significantly degrade the flow in the inter-vane channel. This results in a phenomenon of self-limitation of the free speed.
  • One of the advantages of the present invention is its lightness, its silent operation, its reliability.
  • simple, inexpensive transmissions on the market can be easily adapted to such a turbine, for driving tools between 0 and 60,000 rpm.
  • the present invention is not limited to the embodiments chosen and encompasses any variant within the reach of ordinary skill in the art.
  • the nominal power level of the device then does not vary significantly; on the other hand, the mass flow injected decreases appreciably, this phenomenon characterizing the introduction of a second energy source materialized by the vacuum at the outlet of the ejection channel, to the detriment of the energy source defined by the primary fluid under pressure ; however, the precision of controlling the speed of rotation of the turbine by acting on the pressure Pp of injection of the primary fluid decreases.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Control Of Turbines (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Jet Pumps And Other Pumps (AREA)
  • Supercharger (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Electrically Driven Valve-Operating Means (AREA)
  • Control Of Water Turbines (AREA)
  • Ultra Sonic Daignosis Equipment (AREA)

Claims (25)

  1. Verfahren zum rotativen Antrieb einer Turbine (12 112, 212, 312), wobei diese Turbine mit einem stromaufwärts gelegenen Zufuhrkanal (11, 111, 211, 311) für ein Fluid und mit einem stromabwärts gelegenen Ausströmkanal (13, 113, 213, 313) verbunden ist, wobei das Verfahren die folgenden Schritte umfaßt:
    - Zuführen eines Sekundärfluids Fs in den Zufuhrkanal (11, 111, 211, 311) für das Fluid, wobei der Zufuhrkanal einen solchen Eingangsquerschnitt aufweist, daß er einen Durchfluß des Sekundärfluids mit großem Massendurchsatz Dms, einer Geschwindigkeit Vs und einem Druck Ps zu erlaubt,
    - simultanes Injizieren eines Primärfluids Fp, das einen Druck Pp und eine Geschwindigkeit Vp, die sehr viel größer sind als die des Sekundärfluids, aufweist und eine vorbestimmte Durchflußrate dmp hat, auf eine solche Weise, daß man im Zufuhrkanal (11, 111, 211, 311) für das Fluid eine homogene Mischung erhält, die einen Massendurchsatz aufweist, der gleich ist der Summe (Dms + Dmp) des Primär- und des Sekundärfluids und eine zur Turbine (12, 112, 212, 312) gerichtete Strömungsgeschwindigkeit, die bezüglich der Geschwindigkeit des Primärfluids Fp gering ist,
    - in Rotation Versetzen der Turbine durch den Durchgang der Fluidmischung durch Flügel (18, 118, 218, 318) dieser Turbine und
    - Ausstoßen der Fluidmischung mit Hilfe eines Ausströmkanals (13, 113, 213, 313) für das Fluid, dessen Ausgangsquerschnitt sich erweitert, um das Druckniveau am Ausgang im wesentlichen an den des außerhalb des Ausströmquerschnittes vorliegenden Fluids anzupassen.
  2. Verfahren nach Anspruch 1, um eine Turbine mit veränderlicher Geschwindigkeit in Drehung zu versetzen, dadurch gekennzeichnet, daß es darüber hinaus noch darin besteht:
    - kontinuierlich eine Größe zu messen, die für die momentante Drehgeschwindigkeit ω der Turbine repräsentativ ist,
    - diese Momentandrehgeschwindigkeit mit der Solldrehgeschwindigkeit zu vergleichen,
    - kontinuierlich einen oder mehrere Strömungsparameter so zu verändern, daß der Nominalbetriebspunkt der Turbine dem vorbestimmten Betriebspunkt entspricht.
  3. Verfahren nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß die Bestimmung des Nominalbetriebspunktes besteht im:
    - Verändern eines Zuflußquerschnittes (351) des Sekundärfluids im Zufuhrkanal und/oder im
    - Verändern eines Injektorquerschnittes (358) des Primärfluids im Zufuhrkanal und/oder im
    - Modifizieren eines Querschnittes des Ausflußkanal des Fluides und/oder im
    - Modifizieren des Injektordruckes des Primärfluides.
  4. Verfahren nach einem der Ansprüche 1 oder 3, dadurch gekennzeichnet, daß man das Primärfluid Fp durch Einspritzung an der Wand in den Zufuhrkanal (11, 111, 211, 311) injiziert.
  5. Verfahren nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß man das Primärfluid Fp durch Wandeinspritzung entlang axialer Richtung in den Zufuhrkanal (11, 111, 211, 311) injiziert.
  6. Verfahren nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß man das Primärfluid Fp so injiziert, daß die Mischung des Primär- und Sekundärfluids in einer Schraubenbewegung erfolgt.
  7. Verfahren nach Anspruch 6, dadurch gekennzeichnet, daß die Schraubbewegung entlang der Wand erfolgt.
  8. Verfahren nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß man das Primärfluid in Ringform in den Zufuhrkanal injiziert.
  9. Verfahren nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß man ein Primärfluid Fp verwendet, das im Bereich eines Injektionsquerschnittes (372) vor der Einbringung in den Zufuhrkanal (311) deutlich Überschallgeschwindigkeit aufweist.
  10. Verfahren nach Anspruch 9, dadurch gekennzeichnet, daß es darin besteht, die Primär- und Sekundärfluide mittels Entspannungswellen, die durch das mit Überschall strömende Primärfluid in der Nachbarschaft seiner Einbringung in den Zufuhrkanal geschaffen werden, zu mischen.
  11. Verfahren nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß es darüberhinaus darin besteht, die Winkel α und β der Fluidmischung in einer Ebene am Eingang der Turbine zu kalibrieren.
  12. Verfahren nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß man eine Größe mißt, die für die Drehgeschwindigkeit ω der Turbine repräsentativ ist, indem man den statischen Druck stromaufwärts und stromabwärts der Turbine (12, 112, 212, 312) mißt.
  13. Verfahren nach einem der vorstehenden Ansprüche, bei dem man die Geschwindigkeit der Fluidmischung erhöht, indem man sie stromaufwärts der Turbine (12, 112, 212, 312) durch einen konvergierenden Kanal (16, 116, 216, 316) fließen läßt.
  14. Turbinenvorrichtung, die das Verfahren nach einem der Ansprüche 1 bis 13 durchführt, umfassend:
    - eine Turbine (12, 112, 212, 312), ein stromaufwärts gelegener Zufuhrkanal (11, 111, 211, 311) für ein Fluid, das zur Turbine fließt und einen stromabwärts gelegenen Ausströmkanal (13, 113, 213, 313) des Fluids, die innerhalb eines im wesentlichen Drehsymmetrie aufweisenden Körper untergebracht sind,
    - Injektionsmittel (14, 114, 214, 314), um ein Primärfluid Fp mit vorbestimmtem Druck, Geschwindigkeit und Massendurchsatz Dmp in den Zufuhrkanal für das Fluid zu injizieren,
    - Zufuhrmittel im Zufuhrkanal für das Fluid, um ein Sekundärfluid Fs mit dem Massendurchsatz Dms einzubringen,
    - der Zufuhrkanal (11, 111, 211, 311) für das Fluid weist einen Eingangsquerschnitt auf, der es erlaubt, eine Strömung des Sekundärfluids mit großem Massendurchsatz Dms, einer Geschwindigkeit vs und einem Druck Ps zu erzeugen,
    - die Injektionsmittel (14, 114, 214, 314) sind so ausgelegt, daß sie ein Primärfluid Fp zuführen, das einen Druck und eine Geschwindigkeit aufweist, die wesentlich größer sind als die des Sekundärfluids und sind so angeordnet, daß sie es erlauben, im Inneren des Zufuhrkanals für das Fluid eine homogene Mischung zu erhalten, die einen großen Massendurchsatz gleich der Summe (Dms + Dmp) des Primär- und Sekundärfluids aufweist, und eine Strömungsgeschwindigkeit zur Turbine (12, 112, 212, 312), die im Vergleich zur Geschwindigkeit des Primärfluids Fp gering ist,
    - der Auslaßkanal (13, 113, 213, 313) weist einen Auslaßquerschnitt auf, der es erlaubt, das Druckniveau im Auslaß im wesentlichen dem des außerhalb des Auslaßquerschnittes vorhandenen Fluids anzupassen.
  15. Vorrichtung nach Anspruch 14, dadurch gekennzeichnet, daß sie so ausgebildet ist, daß sie die Turbine mit vorgegebener variabler Geschwindigkeit antreibt, wobei die Vorrichtung weiters Regel- und Steuermittel (50) aufweist, umfassend:
    - Mittel (19) zum Messen einer Größe, die der Drehgeschwindigkeit ω der Turbine entspricht,
    - Aufnahmemittel (20) für die gemessene Drehgeschwindigkeit,
    - Behandlungsmittel (21), die so ausgebildet sind, daß sie die gemessene Drehgeschwindkeit mit einer vorgegebenen Drehgeschwindigkeit vergleichen,
    - Betätigungsorgane (51), die so ausgebildet sind, daß sie funktionelle und/oder dimensionelle Parameter der Strömung regulieren (21), um den gemessenen Drehgeschwindigkeitswert mit dem vorbestimmten Wert dieser Geschwindigkeit in Einklang zu bringen und mit
    - einem Absperrventil (22).
  16. Vorrichtung nach Anspruch 14 oder 15, wobei das Injektionsmittel (14) ein Injektor mit Querschnittsvergrößerung ist.
  17. Vorrichtung nach Anspruch 14 oder 16, dadurch gekennzeichnet, daß das Injektionsmittel (114, 214) zumindest eine Leitung (130, 230) aufweist, die so ausgebildet ist, daß sie das Primärfluid entlang der Wand des Zufuhrkanals einbringt.
  18. Vorrichtung nach Anspruch 14 oder 15, dadurch gekennzeichnet, daß das Injektionsmittel (114) zumindest eine Leitung (130) mit gegebener Neigung α bezüglich einer Achse A des Zufuhrkanals und einer Neigung β bezüglich einer Achse F des Zufuhrkanals aufweist, so ausgewählt, daß das Primärfluid Fp dem Zufuhrkanal in einer schraubförmigen Bahn zugeführt wird.
  19. Vorrichtung nach Anspruch 14 oder 15, dadurch gekennzeichnet, daß das Injektionsmittel (314) aus einem Ringraum im Inneren des Zufuhrkanals besteht, wobei dieser Ringraum einen konvergierenden Abschnitt, einen Abschnitt mit veränderlicher Breite (358) und einen divergierenden Abschnitt aufweist.
  20. Vorrichtung nach einem der Ansprüche 14 bis 19, dadurch gekennzeichnet, daß der Auslaßkanal (13, 113, 213, 313) radial und/oder axial angeordnet ist.
  21. Vorrichtung nach einem der Ansprüche 14 bis 20, dadurch gekennzeichnet, daß die Meßmittel aus zumindest zwei Aufnehmern (19) bestehen, die in der Lage sind, die statischen Drücke stromaufwärts und/oder stromabwärts der Turbine zu messen.
  22. Vorrichtung nach einem der Ansprüche 14 bis 21, dadurch gekennzeichnet, daß sie weiters umfaßt:
    - ein Betätigungsorgan (355), das in der Lage ist, den Querschnitt des Injektors für das Primärfluid zu verändern und/oder
    - ein Betätigungsorgan (353), das in der Lage ist, den Querschnitt der Zufuhr des Sekundärfluids zu verändern und/oder
    - ein Betätigungsorgan (354), das in der Lage ist, den Auslaßquerschnitt der Fluidmischung zu verhindern.
  23. Vorrichtung nach Anspruch 22, dadurch gekennzeichnet, daß jedes Betätigungsorgan (353, 354, 355) durch das Regelorgan (21) betätigt wird.
  24. Vorrichtung nach einem der Ansprüche 14 bis 23, dadurch gekennzeichnet, daß die Drehachse der Turbine aus einem Schaft (160) eines durch die Turbine angetriebenen Werkzeugs (180) besteht.
  25. Vorrichtung nach einem der Ansprüche 14 bis 24, dadurch gekennzeichnet, daß die Turbine und/oder ein stromaufwärts gelegener Verteiler mit Flügeln versehen sind, die konstante Bogenlänge aufweisen, im Zylinderschnitt mit einem Zylinder, der die gleiche Achse wie die Turbine hat, konstante Dicke aufweisen, deren Winkel der Eintrittskanten konstant sind, deren Winkel der Austrittskanten konstant sind, wobei die gekrümmten Oberflächen des Intrado und Extrado durch eine konische Oberfläche geschaffen werden, deren Scheitel der Schnittpunkt der Achse der Turbine mit den normal zur Turbinenachse verlaufenden Ebenen ist, mit der Eintrittsebene für den stromaufwärts gelegenen Teil und mit der Austrittsebene für den stromabwärts gelegenen Teil, wobei der Scheitelwinkel eine Funktion des Winkels der Eintrittskante für den stromaufwärts gelegenen Teil und des Winkels der Austrittskante für den stromabwärts gelegenen Teil ist.
EP92922988A 1991-10-11 1992-10-09 Verfahren, um eine turbine mittels eines strahlapparates anzutreiben Expired - Lifetime EP0607357B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR9112711A FR2682428B1 (fr) 1991-10-11 1991-10-11 Dispositif de commande et de controle en rotation d'une turbine pneumatique.
FR9112711 1991-10-11
PCT/FR1992/000957 WO1993007361A1 (fr) 1991-10-11 1992-10-09 Procede d'entrainement en rotation d'une turbine par un dispositif ejecteur

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EP0607357A1 EP0607357A1 (de) 1994-07-27
EP0607357B1 true EP0607357B1 (de) 1997-03-12

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CA (1) CA2121029C (de)
DE (1) DE69218232T2 (de)
ES (1) ES2101877T3 (de)
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WO (1) WO1993007361A1 (de)

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EP0607357A1 (de) 1994-07-27
AU2907492A (en) 1993-05-03
FR2682428B1 (fr) 1993-12-24
WO1993007361A1 (fr) 1993-04-15
CA2121029C (en) 2004-02-03
JPH06511528A (ja) 1994-12-22
US5553995A (en) 1996-09-10
FR2682428A1 (fr) 1993-04-16
JP3320718B2 (ja) 2002-09-03
ATE150133T1 (de) 1997-03-15
ES2101877T3 (es) 1997-07-16
CA2121029A1 (en) 1993-04-15
AU673658B2 (en) 1996-11-21
DE69218232T2 (de) 1997-10-09
DE69218232D1 (de) 1997-04-17

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