EP2659093A1 - Turbomachine - Google Patents

Turbomachine

Info

Publication number
EP2659093A1
EP2659093A1 EP11802969.3A EP11802969A EP2659093A1 EP 2659093 A1 EP2659093 A1 EP 2659093A1 EP 11802969 A EP11802969 A EP 11802969A EP 2659093 A1 EP2659093 A1 EP 2659093A1
Authority
EP
European Patent Office
Prior art keywords
impeller
working medium
edge
channel
turbomachine
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
EP11802969.3A
Other languages
German (de)
French (fr)
Other versions
EP2659093B1 (en
Inventor
Frank Eckert
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.)
Duerr Cyplan Ltd
Original Assignee
Duerr Cyplan Ltd
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
Priority claimed from DE202010017157U external-priority patent/DE202010017157U1/en
Priority claimed from DE201010056557 external-priority patent/DE102010056557A1/en
Application filed by Duerr Cyplan Ltd filed Critical Duerr Cyplan Ltd
Priority to EP18209322.9A priority Critical patent/EP3480425B1/en
Publication of EP2659093A1 publication Critical patent/EP2659093A1/en
Application granted granted Critical
Publication of EP2659093B1 publication Critical patent/EP2659093B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/54—Fluid-guiding means, e.g. diffusers
    • 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
    • F01D1/08—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 having inward 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
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/30—Exhaust heads, chambers, or the like
    • 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
    • F05D2240/00—Components
    • F05D2240/20—Rotors
    • F05D2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
    • F05D2240/302—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor characteristics related to shock waves, transonic or supersonic flow

Definitions

  • the invention relates to a turbomachine, in particular a turbine, with a housing which has at least one inflow channel, and with a rotatably mounted in the housing on a shaft impeller on which a plurality of blades are arranged, which are flowed by a working medium, wherein the working medium via the inflow channel flows into at least one formed between two blades received on the impeller blades formed channel.
  • the invention also relates to an energy conversion plant which makes use of a cyclic process for the provision of mechanical energy, in which a working medium is thermodynamically expanded almost isentropically by means of a thermal turbomachine (turbine).
  • a thermal turbomachine turbine
  • FIG. 1 is a sectional view of a portion of a conventional steam turbine in the form of a radial turbine, which is designed for a vapor flow below the sound velocity (subsonic flow).
  • a radial turbine the corresponding working medium flows in the radial direction with respect to an axis of rotation of an impeller and acts on the blade at the edge of this impeller.
  • the working medium is flowed in the axial direction with respect to a rotational axis of the impeller.
  • Fig. 1 shown turbine are formed by the radial in the axial direction at an angle of 90 ° extending blade inlet and -austrittskanten.
  • the turbomachine of FIG. 1 designed as a radial turbine has an essentially stationary turbine housing 110, in which a turbine wheel 120 (impeller) is arranged.
  • the impeller 120 includes a plurality of (co-rotating) blades, wherein in Fig. 1 representative of a blade 121 is shown.
  • a gaseous working medium for example exhaust gas from an internal combustion engine, flows through an inflow channel or through a nozzle channel 100 of the turbine housing 110 according to a directional arrow 151 and drives the impeller 120.
  • the flowing working fluid is first accelerated in the nozzle channel 1 10 and deflected along a blade 121, wherein the edges of the blade are aligned on the one hand in the region of a working medium inlet parallel to the axis of rotation of the impeller 120 and have a working medium outlet 153 in the radial direction.
  • the working medium is guided along its entire flow path in the impeller between vanes 121.
  • the impeller 120 of the flow device (turbine) according to FIG. 1 is fundamentally similar to the impeller of a compressor, in which the working medium driven by the blades flows in a direction oriented opposite to the illustration according to FIG. Accordingly, the flow can be deflected in an operating state as a compressor within the blades of the impeller from the inside out so that it runs after exiting the blade channels at Hämediumaustritt axially to the impeller.
  • This type of paddle wheels or blading is well suited for working medium or vapor velocities below the speed of sound.
  • radial turbines according to the prior art with wheels in which the flow is deflected along its blading by 90 °, give Difficulties when steam flows reach their speed of sound.
  • a particular problem is that radial turbines for supersonic flows with parallel and axially directed to the shaft blades lead to vortex formation and thereby lose effectiveness.
  • the Organic Rankine cycle process is a process of energy conversion in which a working fluid other than water vapor is used from a heat source to operate steam turbines.
  • a working medium mostly organic liquids are used with a lower evaporation temperature (T V erd ⁇ 100 ° C), rarely with a higher evaporation temperature.
  • the method is used primarily in power generation and energy conversion plants when the available temperature gradient between the heat source and the heat sink is too low for the operation of a water vapor driven turbine.
  • a turbomachine according to the invention has a housing with an inflow channel.
  • a rotatably mounted on a shaft impeller is arranged, which has a plurality of flowable by the working medium blades.
  • a special feature of a turbomachine according to the invention is that a guide body with at least one deflection element is provided in the intermediate region between the blade channel outlet and the outlet channel for a deflection of the working medium flowing out of a blade channel in the direction of the outlet channel.
  • the working fluid first flows into the impeller via the inflow passage in the radial direction with respect to an axis of rotation of the impeller.
  • the blades of the impeller thereby form a grid rotating with the impeller and subdivided in the circumferential direction of the impeller, in which the working medium is deflected in particular in the circumferential direction and directed in the radial direction into the interior of the impeller.
  • rectangular inlet openings of a plurality of blade channels are formed between the radially outer edges of the blades and rectangular outlet openings of a plurality of blade channels are formed between the radially inner edges of the blades.
  • the inlet and outlet openings of a blade channel are each arranged in planes which are parallel to one another or at an acute angle to one another.
  • the intermediate region (co-rotating) according to the invention is arranged in the interior of the impeller such that it is at least partially surrounded annularly by the outlet openings of a plurality of vane channels.
  • the guide body preferably has a deflection element in the form of an integrally formed with the impeller shaft support structure with rotationshyperboloider or conical outer contour (impeller cone), which serves on its outer side for flow deflection.
  • the guide body also has an annular deflection element in the form of a circular ring structure, which is at least partially inserted into the intermediate space.
  • a guidance body with all sections rotatably connected to the impeller may have both stationary and non-moving baffles connected to the impeller.
  • annular deflecting element engaging in the interspace can be fixed via a fastening ring on the housing of the turbomachine.
  • the mounting ring is then preferably designed as a disk-shaped, fürström bare grid structure with radially extending spokes. In this case, the axial force acting on the paddle wheel resulting from the directional change of the flow is reduced.
  • the turbomachine is designed as a compressor, in which the working fluid, due to the function, flows contrary to the direction flowing in a turbine.
  • the working medium flows into the impeller via a widening inflow channel (in relation to the rotational axis of the impeller) in the radial direction.
  • a bottleneck is for the Stream of the working medium in the region of the inflow channel is preferred in order to achieve supersonic speed in the region of the inflow channel can.
  • the guide body has a deflecting element with a first and a second annular edge, wherein the first annular edge of the deflecting element is positioned adjacent to the Schaufelkanalaustritt and wherein the second annular edge is positioned adjacent to the diffuser channel entrance.
  • the deflecting element is designed such that the first edge is a leading edge and in (relative to the impeller) radial direction, wherein the second edge is a trailing edge and facing in the same direction as the axis of rotation, so that so that the effluent from the blade channel working fluid is deflected from the radial to the axial direction.
  • the guide body has a plurality of spaced-apart deflection elements.
  • the deflecting element comprises a side facing the impeller and a side facing away from the impeller.
  • the deflecting element is here positioned such that it can be flowed around on both sides of the working medium. Accordingly arise on both sides of the deflecting annular channels for the working fluid.
  • the annular deflecting element is arranged approximately on all sides by working medium umströmbar. More preferably, the annular deflecting element at least in sections on a drop, semi-moon or Tragf liege-shaped cross-sectional geometry. This results in an advantageous deflection of the working medium in the region of the impeller. This enables a particularly efficient operation of the flow device.
  • the guide body on a plurality of spaced deflecting elements, which together form a through-flow grating with annular channels.
  • the total flow of the working medium is divided into a plurality of annular partial streams.
  • the total current can be deflected effectively, wherein the individual partial flows formed can be subjected to different treatments by making the contours of the deflecting elements different from each other.
  • further flow guidance elements such as turbulence promoters, surface coatings or the like can be arranged on the deflection elements. The same effect can basically be achieved even when using only one deflecting element.
  • the deflecting elements spaced from each other are positioned such that their edges facing the blades of the impeller have an axial spacing in the axial direction.
  • the edges facing the blades of the impeller at least approximately the same (outer) diameter, which in turn is smaller by a maximum of 10% than a (common) diameter of the inner edges of the impeller blades.
  • the deflecting elements spaced apart from each other are positioned such that their edges pointing in the direction of the axis of rotation of the impeller have a different radial deflection. stand with respect to the axis of rotation of the impeller.
  • a plurality of permanent magnets and / or rotor windings are arranged on a shaft connected to the impeller, which with a plurality of adjacently arranged, the shaft encircling stator windings form an electrical generator.
  • the turbomachine can be used as a "generator turbine" for power generation.
  • a turbomachine according to the invention may in particular be a thermal turbomachine.
  • An idea of the invention is, moreover, to use a turbomachine according to the invention as a turbine, in particular as a radial turbine, in an Organic Rankine cycle.
  • the invention therefore also extends to a system for converting energy with a cyclic process in which a turbomachine according to the invention is used.
  • the invention relates to a radial turbine for a plant for the conversion of energy in the form of a so-called ORC plant.
  • An ORC plant is a plant in which a thermodynamic cycle in the form of an "Organic Rankine Cycle” (ORC) is performed, with which heat can be converted into mechanical energy.
  • the heat supplied to an ORC system according to the invention can originate, for example, from a heat source in the form of an internal combustion engine from a combined heat and power plant, from a biomass combustion plant, from a geothermal source or from a solar power plant.
  • a heat source in the form of an internal combustion engine from a combined heat and power plant, from a biomass combustion plant, from a geothermal source or from a solar power plant.
  • Any form of waste heat can be used with an ORC system.
  • Systems- example can be obtained from the waste heat of internal combustion engines by means of an ORC plant additional electrical energy.
  • An ORC plant may contain a condenser for liquefying a working medium of the plant, a pump, an evaporator for evaporating the working medium.
  • a turbomachine downstream of the evaporator, in particular a turbine, in which the working fluid is expanded while removing kinetic energy from the circulation.
  • the pump brings a liquid working under standard conditions to operating pressure. Subsequently, the still liquid working medium flows through the heat exchanger (evaporator) or a heat exchanger system in which thermal energy is transferred for example from one of the aforementioned sources to the working medium of the ORC system. Due to the energy input, the working medium preferably evaporates completely. At the outlet of the evaporator then saturated steam or dry steam is formed. The energy input in the evaporator increases the specific volume and the temperature of the steam.
  • volume change work which converts the turbine on their blades into mechanical energy.
  • the steam flows out of the turbine through a regenerator in which a heat exchange takes place between the vaporous working medium and the liquid working medium coming from the pump (internal heat exchange).
  • the (still vaporous) working medium brought to the condensation temperature in the turbine and possibly in the regenerator reaches the downstream condenser, in which the working medium is recondensed with the release of low-temperature heat.
  • the heat released in the condensation is preferably fed via a cooling water circuit in a heat network.
  • the working medium condenses out and returns completely to the liquid state of aggregation.
  • the feed pump (pump) subsequently brings the working fluid to operating pressure and then back into the evaporator. This completes the cycle.
  • a generator can be driven, which generates electrical current with the mechanical energy generated by the turbine from thermal energy.
  • Such an ORC system with a turbomachine according to the invention can be used both for small and large domestic installations as well as for large industrial plants and power plants.
  • house equipment are the power supplies, z.
  • Industrial plants are e.g. Manufacturing plants, in particular manufacturing plants of the automotive industry, in particular paint shops, in which a balanced demand for electricity (from mechanical energy) and heat at different temperature levels is needed.
  • FIGS. 2, 3, 4, 5 a and 5b Advantageous embodiments of a turbomachine according to the invention are shown in FIGS. 2, 3, 4, 5 a and 5b and will be described below. Show it:
  • FIG. 2 shows a sectional view of a radial turbine for supersonic flow with a deflecting element in the form of a hyperboloid of revolution (impeller cone) for deflecting the flow within the impeller;
  • FIG 3 is a sectional view of an impeller of a radial turbine for supersonic flow with a sectionally projecting into the impeller guide body for reducing the vortex formation in a downstream diffuser.
  • FIG. 4 shows a sectional view of a flow device with guide bodies located mainly within the rotor wheel
  • Fig. 5a is an enlarged sectional view of a portion of the flow device of Fig. 4; and Fig. 5a shows a view of vanes of the impeller of the flow device according to the invention from Fig. 5a, which are shown cut to illustrate their geometry transversely to the blade axis.
  • Fig. 2 shows a section of a sectional view of a turbomachine according to the invention in the form of a radial turbine with a substantially stationary turbine housing 1, 4, 1 1, in which a turbine wheel 2 (impeller) is arranged.
  • the turbine housing 1, 4, 1 1 comprises in particular a nozzle ring 1 and an associated cover 1 1.
  • the cover 1 1 and the nozzle ring 1 are preferably designed as separate modules. Between them, the nozzle channels 10 are formed.
  • the turbine housing 1, 4, 1 1 comprises a diffuser 4 with an outlet channel 40 for the working medium.
  • the impeller 2 disposed in the turbine housing includes a plurality of (co-rotating) vanes.
  • the impeller 2 is shown with a blade 21.
  • Between the blades of the impeller 2 straight or curved blade channels 20 are formed, which have a substantially rectangular cross-section.
  • the blades are connected to each other via a base of the impeller 2 and on a side spaced therefrom via a so-called bandage 22.
  • a vaporous working medium for example the working medium of an ORC system, flows through a nozzle channel 10 of the turbine housing 1 1 acting as an inflow channel in accordance with a directional arrow 51.
  • the flowing working medium is accelerated via a corresponding nozzle geometry, so that sound velocity is reached at a constriction, wherein the working medium can be brought to supersonic speed before being transferred to the impeller 2.
  • the vaporous working medium flows out of the nozzle channel 10 and impinges on the blade 21, which is designed in such a way that both the flowed edge and the downstream edge of the blade 21 and therefore also these are aligned parallel to and axially towards the impeller shaft.
  • the majority of the stream 51 of working medium is after passing through the blades 21 or a respective blade channel between see several blades 21 (and thus in a so-called intermediate region of the impeller 2) deflected parallelism to the axis of rotation of the impeller (arrow 53).
  • a guide body 3 in Form of a conical deflecting element (impeller cone) provided, which is preferably designed as a rotational hyperboloid.
  • This deflecting element can optionally be designed in one piece with the impeller.
  • the guide body 3 is located in an intermediate region 29 between the blade channel outlet 23 and the inlet opening 24 in the outlet channel 40 formed by the diffuser 4.
  • the deflecting element with the guide body 3 designed as an impeller cone is in the region of its base in the intermediate region 29 within the Impeller 2 arranged. It is enclosed in sections annularly by the blade channel outlets 23 and by the blades 21 of the rotor.
  • the guide body 3 extends into the outlet channel 40 formed by the diffuser 4.
  • the impeller cone causes a largely laminar flow deflection at moderate flow velocities. At high flow velocities, vortices 54 can occur.
  • the positioning of guide bodies in the outflow channel or in the diffuser 4 behind the impeller 2 can reduce vortex formation.
  • FIG. 3 is essentially the same as the flow device according to FIG. 2. Accordingly, reference can be made to the above description to Fig. 2 reference. Accordingly, similar components and functional units are provided with the same reference numerals.
  • the flow apparatus according to FIG. 3 comprises, in addition to a first deflection element in the form of the co-rotating impeller cone, a second deflection element 31 in the form of a ring-shaped guide body 3 mounted on the housing side.
  • the guide body 3 ' preferably engages in an intermediate region 29 of the impeller 2, which differs from the one Impeller blades 21 is encompassed. As a result, the stream of working fluid emerging from the impeller blade channels can be split early into two annular partial streams.
  • the guide body 3 ' has a first and a second annular edge 25, 26.
  • the first edge 25 of the deflection element is positioned adjacent to the blade channel exit 23 within the intermediate region 29.
  • the second edge 26 is arranged adjacent to the inlet opening 24 within the outlet channel 40.
  • the first edge 25 acts as a leading edge.
  • the second edge 26 is a trailing edge.
  • the deflecting element 31 is formed with a guide contour 28, which extends from the first edge 25 from an approximately to a rotational axis 27 of the impeller 2 radial direction to the second edge 26 in an approximately to the axis of rotation 27 of the impeller 2 axial direction.
  • the effluent from the blade channel 20 working fluid is thus deflected by the deflecting element 31 from a substantially radial in a substantially axial direction.
  • other flow directions can be generated by the contours of the deflecting elements are oriented in the corresponding directions.
  • radial turbines are often used in ORC plants for converting the flow energy of the working medium into a torque. Due to the low sound velocity in such media and the high pressure ratios between the inlet and outlet of the steam in the turbine, the flow velocity of the steam in the impeller of the turbine is often above the speed of sound. Also, the exit velocity of the steam from the impeller is often still over Mach 0.7.
  • FIGS. 4, 5a and 5b are sections of a further inventive, designed as a radial turbine flow machine shown, the nozzle ring 1 with a nozzle cover 1 1, mounted in a housing on a shaft impeller 2, an inflow passage 10, a diffuser 4, a plurality of blades arranged on the impeller 2, a first lattice-shaped guide body 3 " and a second conical guide body 3.
  • a basic mode of operation corresponds to that of the radial turbine according to Fig. 2 or Fig. 3, so that reference is made to the statements made for this purpose can be.
  • a vaporous working medium can be conducted via the inflow passage 10 to a wheel entry of the impeller according to a directional arrow 51. It hits the blade 21 there and flows between the blades 21 into a blade channel 20 according to a directional arrow 42 (FIG. 5b). The flow onto the blade 21 takes place in the radial direction with respect to a rotational axis of the impeller 2. After flowing through the blade channel 20, the working fluid passes into an intermediate region 29 between a blade channel outlet and an outlet channel 40 downstream of the rotor 2.
  • the first guide body 3 " and the second guide body 3 are positioned, whereby both guide bodies can preferably extend in sections out of the intermediate area into the outlet channel 40.
  • the first guide body 3 " also comprises a lattice-shaped, in particular provided with radial spokes, permeable mounting ring 34 two annular deflecting elements 31 and 32, wherein in alternative embodiments, more than two deflecting elements are usable. Alternatively, a single annular deflecting element 31 may also be provided.
  • the annular deflection elements 31, 32 are preferably carried integrally excluded together with the mounting ring 34 and thus form the first guide body 3 ", which may also be referred to as a flow grid.
  • the thus constructed first guide member 3 ' engages with the second guide member 3 in the form of Impeller cone together: both guide body 3, 3 " cooperatively share the intermediate region 29 of the impeller 2 at least in sections into separate annular flow channels.
  • the working medium is accordingly divided several times immediately after the blades 21 by the deflecting elements 31 and 32 of the first guide body 3 " and for the most part still directed within the blade wheel 2 parallel to its axis of rotation according to a directional arrow 53.
  • the first guide body 3 extends between a first 25 and a second edge 26 of a deflection element 31 or 32 and is designed such that the first edge is positioned adjacent to the blade channel exit, wherein the second edge 26 is positioned adjacent to the diffuser channel entrance 40 is.
  • the deflection element 31, 32 is formed such that the first edge 25 serves as leading edge and in the radial direction to the axis of rotation of the impeller 2, wherein the second edge 26 is a trailing edge and facing in the same direction as the axis of rotation, so that from the working fluid flowing from the blade channel 20 is deflected from a radial to an approximately axial direction.
  • Both deflecting elements 31, 32 each have a side facing the impeller 2 and a side facing away from the impeller 2.
  • the deflecting elements 31, 32 are in particular so positioned that they are flow around the working medium on both sides.
  • the working medium is deflected after its exit from the bluff channel 20 in such a way in the diffuser channel 40 that a flow along the impeller 2 is optimized.
  • the deflecting elements 31 and 32 of the first guide body 3 " preferably have crescent-shaped cross-sectional contours, the profile of which has a favorable flow configuration.
  • the first edge (annular leading edge) pointing towards the impeller 2 points radially away from the center
  • the second edge located on the axial opposite side (annular trailing edge) points away from the impeller base 2.
  • the curvature of the profile of the deflecting elements is designed so that the working medium is continuously deflected parallel to the axis of rotation of the impeller 2.
  • the trailing edges of these deflecting elements 31, 32 have different diameters with respect to the axis of rotation of the impeller 2, while it is expedient that the leading edges have the same diameter with respect to a rotational axis of the impeller 2
  • the leading edges are positioned as close as possible to the exit edges of the blades 21.
  • the (substantially equal) diameter of the leading edges of the deflecting elements 31, 32 have a diameter which is less than 10% smaller than the diameter of the circle touching all the exit edges of the blades.
  • each blade 21 has a blade height 60 at the blade channel outlet within the rotor 2.
  • a first axial distance 61 between see a surface of the impeller base and the inflow edge of the (first) deflecting element 31 is smaller than an axial distance between the leading edge of the (second) deflecting element 32 and the same surface the impeller base, so that between the leading edges of both deflecting elements 31, 32 an axial distance 62 is present.
  • the leading edge of the deflecting element 32 to the drum 22 is spaced by an axial distance 63.
  • the mutually adjacent deflecting elements 31, 32 are positioned such that their trailing edges 26 have a different radial distance with respect to the axis of rotation of the impeller 2.
  • the leading edges facing the blades of the impeller have a different axial distance 61 or distance 61 +62 to the impeller base in the axial direction.
  • the impeller 2 is the rotating part of the turbomachine or the radial turbine, which either extracts work from the flowing working medium when using the turbomachine as a turbine or work feeds when using the turbomachine as a compressor.
  • the impeller 2 is connected to a shaft, not shown, is discharged through the generated mechanical energy.
  • downstream diffuser 4 is slowed by expansion of the flow cross section, the gas flow and increases the static gas pressure.
  • the diffuser 4 represents in principle the inversion of a nozzle.
  • a bandage 22 shown in Fig. 5a is arranged on the blades 21 and serves to stabilize the impeller 2 and to keep it in shape.
  • the guide body 3 or the deflecting elements 31 and 32 are preferably connected via webs 33 to the turbine housing or the diffuser 4 of the turbine, so that the forces acting on account of the diversion of the working medium are not transmitted to the impeller shaft.
  • the guide body 3 is the counterpart to the moving impeller 2, wherein the guide body 3 preferably fixed to the housing or on the diffuser 4 via the webs 33 is formed. Accordingly, the impeller 2 and the guide body 3 together form a step.
  • a fastening ring 34 of the guide body 3 is provided on the diffuser inlet. It is also possible to attach the deflecting elements 31 and 32 to the impeller 2, so that they then co-rotate.
  • a deflecting element may be fixed to the impeller and another to the housing.
  • the guide body 3 " or the deflecting elements 31 and 32 in a turbomachine according to the invention are made of a (noble) steel and are produced by means of machining processes, but these can in principle also be produced from cast metal (cast aluminum, cast steel, cast iron)
  • the turbomachine is used as a radial turbine in an ORC plant for performing an Organic Rankine cycle.
  • a turbomachine in particular, in which a vaporous working medium flows under a pressure, is expanded in a stationary nozzle system, even with a guide blade, and in this process is accelerated.
  • the steam is deflected therein by a rotating blade system, possibly further relaxed and gives off its flow energy through the blades to a shaft connected to the blades or coupled. From this shaft, the mechanical rotational energy is then transferred to a consumer or a means for converting energy for further use.
  • devices for converting energy in the form of generators for power generation can be driven by the shaft.
  • the invention causes with simple and inexpensive Leit Congress an increase in efficiency of radial turbines.
  • a turbomachine in particular a turbine, comprises a housing 1, 4, 11, which has at least one inflow passage 10.
  • a plurality of blades are arranged on an impeller 2, which can be flowed against by a working medium.
  • the working medium in this case flows via the inflow passage 10 into at least one vane passage 20 formed between two vanes 21 accommodated on the impeller 2. After exiting the impeller area, the working medium enters a diffuser 4.
  • At least one guide body 3, 3 ' , 3 " is provided for a deflection of the working medium flowing out of the blade channel 20 in the direction of the diffuser 4.
  • the guide body in the turbomachine is preferably at least partially in an intermediate region 29 of the radial direction surrounded by the impeller blades Impeller positioned between a blade channel outlet 23 and an inlet opening 24 in a downstream of the impeller 2 formed by the diffuser 4 outlet channel 40.
  • the invention also relates to a system for performing an Organic Rankine cycle with such a turbomachine.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

The invention relates to a turbomachine, in particular a turbine, comprising a housing which has at least one inflow channel (10). A plurality of blades is arranged on a rotor (2) and a working medium flows towards said blades. The working medium flows via the inflow channel (10) into at least one blade channel (20) which is formed between two blades (21) that are accommodated on the rotor (2). After exiting the rotor region, the working medium enters a diffuser (4). At least one guide body (3, 3'') is provided for deflecting the working medium which flows out of the blade channel (20) in the direction of the diffuser (4). At least some sections of the guide body in the turbomachine are preferably positioned in an intermediate region (29) of the rotor (2), which intermediate region (29) is surrounded in the radial direction by the rotor blades (21) and lies between a blade-channel outlet (23) and an inlet opening (24) in an outlet channel (40) which is connected downstream of the rotor (2) and is formed by the diffuser (4). The invention also relates to a system for carrying out an organic Rankine cycle process by means of a turbomachine of this type.

Description

Strömungsmaschine  flow machine
Die Erfindung betrifft eine Strömungsmaschine, insbesondere eine Turbine, mit einem Gehäuse, das zumindest einen Einströmungskanal aufweist, und mit einem in dem Gehäuse auf einer Welle drehbar gelagerten Laufrad, an dem mehrere Schaufeln angeordnet sind, die von einem Arbeitsmedium anströmbar sind, wobei das Arbeitsmedium über den Einströmungskanal in mindestens einen zwischen zwei am Laufrad aufgenommenen Schaufeln gebildeten Schaufelkanal einströmt. The invention relates to a turbomachine, in particular a turbine, with a housing which has at least one inflow channel, and with a rotatably mounted in the housing on a shaft impeller on which a plurality of blades are arranged, which are flowed by a working medium, wherein the working medium via the inflow channel flows into at least one formed between two blades received on the impeller blades formed channel.
Die Erfindung betrifft außerdem eine Energieumwandlungsanlage, die zur Bereitstellung von mechanischer Energie von einem Kreisprozess Gebrauch macht, bei dem ein Arbeitsmedium mit Hilfe einer thermischen Strömungsmaschine (Turbine) thermodynamisch nahezu isentrop entspannt wird. The invention also relates to an energy conversion plant which makes use of a cyclic process for the provision of mechanical energy, in which a working medium is thermodynamically expanded almost isentropically by means of a thermal turbomachine (turbine).
Eine solche erfindungsgemäße Strömungsmaschine ist in der deutschen Gebrauchsmusteranmeldung DE 20 2010 017 157.1 mit der Gebrauchsmusterschrift DE 20 2010 017 157 U1 und der am 30.12.2010 angemeldeten deutschen Patentanmeldung DE 10 2010 056 557.1 beschrieben, auf die hiermit Bezug genommen und deren Offenbarungen in die Beschreibung dieser Erfindung in vollem Umfang einbezogen wird. Such a turbomachine according to the invention is described in the German utility model application DE 20 2010 017 157.1 with the utility model DE 20 2010 017 157 U1 and the German patent application DE 10 2010 056 557.1 filed on 30.12.2010, to the hereby incorporated and their disclosures in the description this invention is fully incorporated.
Eine als Radialturbine ausgebildete Strömungsmaschine gemäß dem Stand der Technik ist in der Fig. 1 gezeigt. Die Fig. 1 ist eine Schnittansicht eines Abschnitts einer herkömmlichen Dampfturbine in Form einer Radialturbine, die für eine Dampfströmung unterhalb der Schallgeschwindigkeit (Unterschallströmung) ausgelegt ist. Bei einer Radialturbine strömt das entsprechende Arbeitsmedium in radialer Richtung bezüglich einer Rotationsachse eines Laufrads und beaufschlagt die Schaufel am Rande dieses Laufrads. Bei Axialturbinen hingegen wird das Arbeitsmedium in axialer Richtung bezüglich einer Rotationsachse des Laufrads eingeströmt. Bei der in der Fig. 1 gezeigten Turbine sind von der radialen in die axiale Richtung mit einem Winkel um 90° verlaufende Schaufelein- und -austrittskanten ausgebildet. A turbomachine designed as a radial turbine according to the prior art is shown in FIG. 1. Fig. 1 is a sectional view of a portion of a conventional steam turbine in the form of a radial turbine, which is designed for a vapor flow below the sound velocity (subsonic flow). In a radial turbine, the corresponding working medium flows in the radial direction with respect to an axis of rotation of an impeller and acts on the blade at the edge of this impeller. In axial turbines, however, the working medium is flowed in the axial direction with respect to a rotational axis of the impeller. In the in Fig. 1 shown turbine are formed by the radial in the axial direction at an angle of 90 ° extending blade inlet and -austrittskanten.
Die als Radialturbine ausgebildete Strömungsmaschine der Fig. 1 hat ein im Wesentlichen ruhendes Turbinengehäuse 1 10, in dem ein Turbinenrad 120 (Laufrad) angeordnet ist. Das Laufrad 120 umfasst eine Mehrzahl an (mitrotierenden) Schaufeln, wobei in Fig. 1 stellvertretend eine Schaufel 121 dargestellt ist. Ein gasförmiges Arbeitsmedium, beispielsweise Abgas aus einer Brennkraftmaschine, strömt durch einen Einströmungskanal bzw. durch ei- nen Düsenkanal 100 des Turbinengehäuses 1 10 gemäß eines Richtungspfeils 151 und treibt das Laufrad 120 an. Hierzu wird das strömende Arbeitsmedium zunächst im Düsenkanal 1 10 beschleunigt und entlang einer Schaufel 121 umgelenkt, wobei die Kanten der Schaufel einerseits im Bereich eines Arbeitsmediumeintritts parallel zur Rotationsachse des Laufrads 120 ausgerichtet sind und an einem Arbeitsmediumaustritt 153 in radiale Richtung weisen. Das Arbeitsmedium wird dabei entlang seines gesamten Strömungsweges im Laufrad zwischen Schaufeln 121 geführt. The turbomachine of FIG. 1 designed as a radial turbine has an essentially stationary turbine housing 110, in which a turbine wheel 120 (impeller) is arranged. The impeller 120 includes a plurality of (co-rotating) blades, wherein in Fig. 1 representative of a blade 121 is shown. A gaseous working medium, for example exhaust gas from an internal combustion engine, flows through an inflow channel or through a nozzle channel 100 of the turbine housing 110 according to a directional arrow 151 and drives the impeller 120. For this purpose, the flowing working fluid is first accelerated in the nozzle channel 1 10 and deflected along a blade 121, wherein the edges of the blade are aligned on the one hand in the region of a working medium inlet parallel to the axis of rotation of the impeller 120 and have a working medium outlet 153 in the radial direction. The working medium is guided along its entire flow path in the impeller between vanes 121.
Das Laufrad 120 der Strömungsvorrichtung (Turbine) gemäß Fig.1 ist grund- sätzlich ähnlich wie das Laufrad eines Verdichters gestaltet, bei dem das durch die Schaufeln getriebene Arbeitsmedium in einer entgegengesetzt zur Darstellung gemäß Fig. 1 orientierten Richtung einströmt. Entsprechend kann die Strömung in einem Betriebszustand als Verdichter innerhalb der Schaufeln des Laufrades von innen nach außen derart umgelenkt werden, dass sie nach dem Austritt aus den Schaufelkanälen am Arbeitsmediumaustritt axial zum Laufrad verläuft. Diese Bauart von Schaufelrädern bzw. Beschaufelung ist für Arbeitsmedium- bzw. Dampfgeschwindigkeiten unterhalb der Schallgeschwindigkeit gut geeignet. Bei Radialturbinen gemäß dem Stand der Technik, mit Laufrädern, in denen die Strömung entlang ihrer Beschaufelung um 90° umgelenkt wird, ergeben sich Schwierigkeiten, wenn Dampfströmungen ihre Schallgeschwindigkeit erreichen. The impeller 120 of the flow device (turbine) according to FIG. 1 is fundamentally similar to the impeller of a compressor, in which the working medium driven by the blades flows in a direction oriented opposite to the illustration according to FIG. Accordingly, the flow can be deflected in an operating state as a compressor within the blades of the impeller from the inside out so that it runs after exiting the blade channels at Arbeitsmediumaustritt axially to the impeller. This type of paddle wheels or blading is well suited for working medium or vapor velocities below the speed of sound. In radial turbines according to the prior art, with wheels in which the flow is deflected along its blading by 90 °, give Difficulties when steam flows reach their speed of sound.
Ein besonderes Problem besteht darin, dass Radialturbinen für Überschall- Strömungen mit parallelen und axial zur Welle ausgerichteten Schaufeln zur Wirbelbildung führen und dadurch an Effektivität verlieren. A particular problem is that radial turbines for supersonic flows with parallel and axially directed to the shaft blades lead to vortex formation and thereby lose effectiveness.
Es ist daher Aufgabe der vorliegenden Erfindung, eine Strömungsvorrichtung der eingangs genannten Art anzugeben, mit der ein höherer Wirkungsgrad und eine verbesserte Strömungsführung ermöglicht wird. It is therefore an object of the present invention to provide a flow device of the type mentioned, with a higher efficiency and improved flow guidance is made possible.
Des Weiteren ist es Aufgabe der vorliegenden Erfindung, eine Anlage zur Energiewandlung, insbesondere zur Durchführung eines Kreisprozesses, insbesondere eines sogenannten Organic-Rankine-Kreisprozesses, zur Ver- fügung zu stellen, deren Wirkungsgrad insbesondere im Bereich des enthaltenen Entspannungsvorgangs verbessert ist. Furthermore, it is an object of the present invention to provide a plant for energy conversion, in particular for carrying out a cyclic process, in particular a so-called Organic Rankine cycle process, the efficiency of which is improved, in particular in the region of the contained expansion process.
Der Organic-Rankine-Kreisprozess (ORC) ist ein Verfahren zur Energieumwandlung, bei dem aus einer Wärmequelle zum Betrieb von Dampfturbinen ein anderes Arbeitsmedium als Wasserdampf verwendet wird. Als Arbeitsmedium werden meistens organische Flüssigkeiten mit einer niedrigeren Verdampfungstemperatur (TVerd < 100°C), selten mit einer höheren Verdampfungstemperatur verwendet. Das Verfahren kommt in Energieerzeugungsund Energieumwandlungsanlagen vorwiegend dann zum Einsatz, wenn das zur Verfügung stehende Temperaturgefälle zwischen Wärmequelle und Wärmesenke zu niedrig für den Betrieb einer von Wasserdampf angetriebenen Turbine ist. The Organic Rankine cycle process (ORC) is a process of energy conversion in which a working fluid other than water vapor is used from a heat source to operate steam turbines. As a working medium mostly organic liquids are used with a lower evaporation temperature (T V erd <100 ° C), rarely with a higher evaporation temperature. The method is used primarily in power generation and energy conversion plants when the available temperature gradient between the heat source and the heat sink is too low for the operation of a water vapor driven turbine.
Diese Aufgabe wird zum einen gelöst durch eine Strömungsmaschine mit den Merkmalen des Patentanspruchs 1 sowie zum anderen durch eine Anlage mit den Merkmalen des Patentanspruchs 15. Eine erfindungsgemäße Strömungsmaschine hat ein Gehäuse mit einem Einströmungskanal. In dem Gehäuse ist ein auf einer Welle drehbar gelagertes Laufrad angeordnet, das mehrere, von dem Arbeitsmedium anströmbare Schaufeln aufweist. This object is achieved, on the one hand, by a turbomachine having the features of patent claim 1 and, on the other hand, by a system having the features of patent claim 15. A turbomachine according to the invention has a housing with an inflow channel. In the housing, a rotatably mounted on a shaft impeller is arranged, which has a plurality of flowable by the working medium blades.
Eine Besonderheit einer erfindungsgemäßen Strömungsmaschine ist, dass für eine Umlenkung des aus einem Schaufelkanal ausströmenden Arbeitsmediums in Richtung des Austrittskanals ein Leitkörper mit mindestens einem Umlenkelement im Zwischenbereich zwischen dem Schaufelkanalaus- tritt und dem Austrittskanal vorgesehen ist. Vorzugsweise strömt das Arbeitsmedium zunächst über den Einströmungskanal in radialer Richtung bezogen auf eine Rotationsachse des Laufrades in das Laufrad ein. Die Schaufeln des Laufrades bilden dabei ein mit dem Laufrad rotierendes, in Umfangs- richtung des Laufrades unterteiltes Gitter, in dem das Arbeitsmedium insbe- sondere in Umfangsrichtung umgelenkt und in radialer Richtung in das Innere des Laufrades geleitet wird. Bevorzugt sind zwischen den radial äußeren Kanten der Schaufeln rechteckige Eintrittsöffnungen von mehreren Schaufelkanälen und zwischen den radial innenliegenden Kanten der Schaufeln rechteckige Austrittsöffnungen von mehreren Schaufelkanälen gebildet. Da- bei sind die Eintritts- und Austrittsöffnungen eines Schaufelkanals erfindungsgemäß jeweils in Ebenen angeordnet, die zueinander parallel sind oder einen spitzen Winkel zueinander aufweisen. Weiter bevorzugt ist der erfindungsgemäße (mitrotierende) Zwischenbereich derart im Inneren des Laufrades angeordnet, dass er zumindest abschnittsweise von den Austrittsöff- nungen mehrerer Schaufelkanäle ringförmig umgeben ist. A special feature of a turbomachine according to the invention is that a guide body with at least one deflection element is provided in the intermediate region between the blade channel outlet and the outlet channel for a deflection of the working medium flowing out of a blade channel in the direction of the outlet channel. Preferably, the working fluid first flows into the impeller via the inflow passage in the radial direction with respect to an axis of rotation of the impeller. The blades of the impeller thereby form a grid rotating with the impeller and subdivided in the circumferential direction of the impeller, in which the working medium is deflected in particular in the circumferential direction and directed in the radial direction into the interior of the impeller. Preferably, rectangular inlet openings of a plurality of blade channels are formed between the radially outer edges of the blades and rectangular outlet openings of a plurality of blade channels are formed between the radially inner edges of the blades. In this case, according to the invention, the inlet and outlet openings of a blade channel are each arranged in planes which are parallel to one another or at an acute angle to one another. More preferably, the intermediate region (co-rotating) according to the invention is arranged in the interior of the impeller such that it is at least partially surrounded annularly by the outlet openings of a plurality of vane channels.
Der Leitkörper weist bevorzugt ein Umlenkelement in Form einer einstückig mit der Laufradwelle ausgeführten Tragstruktur mit rotationshyperboloider oder kegeliger Außenkontur (Laufradkegel) auf, die an ihrer Außenseite zur Strömungsumlenkung dient. Der Leitkörper weist ferner ein ringförmiges Umlenkelement in Form einer Kreisringstruktur auf, die zumindest abschnittsweise in den Zwischenraum eingesetzt ist. Erfindungsgemäß kann ein Leit- körper mit allen Teilabschnitten drehfest mit dem Laufrad verbunden sein. Alternativ kann ein Leitkörper sowohl mit dem Laufrad verbundene mitdrehende als auch mit dem Gehäuse verbundene unbewegte Umlenkelemente aufweisen. The guide body preferably has a deflection element in the form of an integrally formed with the impeller shaft support structure with rotationshyperboloider or conical outer contour (impeller cone), which serves on its outer side for flow deflection. The guide body also has an annular deflection element in the form of a circular ring structure, which is at least partially inserted into the intermediate space. According to the invention, a guidance body with all sections rotatably connected to the impeller. Alternatively, a baffle may have both stationary and non-moving baffles connected to the impeller.
Mit der Anordnung von Umlenkelementen innerhalb des Schaufelrades wird erfindungsgemäß eine Ablösung der Strömung und ein damit verbundener Druckverlust unmittelbar nach dem Schaufelrad minimiert. Die Wirkung eines gegebenenfalls nachgeschalteten Diffusors zur zusätzlichen Effizienzerhö- hung wird verbessert. Dies wird erfindungsgemäß besonders dann erreicht, wenn durch wenigstens ein ringförmiges Umlenkelement der aus den Austrittsöffnungen mehrerer Schaufelkanäle (Schaufelkanalaustritte) austretende Strom an Arbeitsmedium nochmals in mehrere voneinander getrennte Teilströme unterteilt wird. Erfindungsgemäß ergeben sich dabei insbesondere in (bezogen auf das Laufrad) axialer Richtung voneinander getrennte Teilströme, die mittels unterschiedlicher Konturen an Vorder- und Rückseite eines Umlenkelements unterschiedlich geführt werden können. With the arrangement of deflecting elements within the impeller, a detachment of the flow and an associated pressure loss is minimized immediately after the impeller according to the invention. The effect of an optionally downstream diffuser for additional efficiency increase is improved. This is achieved according to the invention particularly when at least one annular deflecting element separates the stream of working medium emerging from the outlet openings of a plurality of blade channels (blade channel outlets) into a plurality of separate partial streams. According to the invention, in particular in (with respect to the impeller) axial direction separate from each other partial streams, which can be performed differently by means of different contours on the front and back of a deflecting.
Weiterhin kann ein in den Zwischenraum eingreifendes ringförmiges Umlenk- element über einen Befestigungsring am Gehäuse der Strömungsmaschine festgelegt sein. Der Befestigungsring ist dann bevorzugt als scheibenförmige, durchström bare Gitterstruktur mit radial verlaufenden Speichen ausgeführt. In diesem Fall wird die auf das Schaufelrad wirkende axiale Kraft reduziert, welche aus der Richtungsänderung der Strömung resultiert. Furthermore, an annular deflecting element engaging in the interspace can be fixed via a fastening ring on the housing of the turbomachine. The mounting ring is then preferably designed as a disk-shaped, durchström bare grid structure with radially extending spokes. In this case, the axial force acting on the paddle wheel resulting from the directional change of the flow is reduced.
Nach einem weiteren Aspekt der Erfindung ist die Strömungsmaschine als Verdichter ausgebildet, bei dem das Arbeitsmedium funktionsbedingt entgegen der bei einer Turbine strömenden Richtung fließt. In einer Ausgestaltung der Erfindung strömt das Arbeitsmedium über einen sich erweiternden Einströmungskanal in (bezogen auf die Rotationsachse des Laufrads) radialer Richtung in das Laufrad ein. Eine Engstelle ist für den Strom des Arbeitsmediums im Bereich des Einströmungskanals bevorzugt, um im Bereich des Einströmungskanals Überschallgeschwindigkeit erreichen zu können. Nach einer Ausgestaltung der Erfindung weist der Leitkörper ein Umlenkelement mit einer ersten und einer zweiten ringförmigen Kante auf, wobei die erste ringförmige Kante des Umlenkelements benachbart zu dem Schaufelkanalaustritt positioniert ist und wobei die zweite ringförmige Kante benachbart zu dem Diffusorkanaleintritt positioniert ist. Hierdurch wird eine vorteil- hafte Abströmung des Arbeitsmediums von dem Laufrad erzielt. Die Folge ist, dass damit eine Wirbelbildung im Austrittsbereich der Strömungsvorrichtung bzw. im Diffusoreintrittsbereich verhindert wird. According to a further aspect of the invention, the turbomachine is designed as a compressor, in which the working fluid, due to the function, flows contrary to the direction flowing in a turbine. In one embodiment of the invention, the working medium flows into the impeller via a widening inflow channel (in relation to the rotational axis of the impeller) in the radial direction. A bottleneck is for the Stream of the working medium in the region of the inflow channel is preferred in order to achieve supersonic speed in the region of the inflow channel can. According to one embodiment of the invention, the guide body has a deflecting element with a first and a second annular edge, wherein the first annular edge of the deflecting element is positioned adjacent to the Schaufelkanalaustritt and wherein the second annular edge is positioned adjacent to the diffuser channel entrance. As a result, an advantageous outflow of the working medium from the impeller is achieved. The consequence is that this prevents vortex formation in the outlet region of the flow device or in the diffuser inlet region.
In einer weiteren Ausgestaltung der Erfindung ist das Umlenkelement derart ausgebildet, dass die erste Kante eine Anströmkante ist und in (bezogen auf das Laufrad) radialer Richtung weist, wobei die zweite Kante eine Abströmkante ist und in die gleiche Richtung wie die Rotationsachse weist, so dass damit das aus dem Schaufelkanal ausströmende Arbeitsmedium von der radialen in die axiale Richtung umgelenkt wird. Hierdurch wird der Wirkungs- grad der Strömungsmaschine verbessert. Vorzugsweise weist der Leitkörper mehrere zueinander beabstandete Umlenkelemente auf. In a further embodiment of the invention, the deflecting element is designed such that the first edge is a leading edge and in (relative to the impeller) radial direction, wherein the second edge is a trailing edge and facing in the same direction as the axis of rotation, so that so that the effluent from the blade channel working fluid is deflected from the radial to the axial direction. As a result, the efficiency of the turbomachine is improved. Preferably, the guide body has a plurality of spaced-apart deflection elements.
Nach einer weiteren Ausgestaltung der Erfindung umfasst das Umlenkelement eine dem Laufrad zugewandte und eine dem Laufrad abgewandte Sei- te. Das Umlenkelement ist hier derart positioniert, dass es von dem Arbeitsmedium beidseitig umströmt werden kann. Entsprechend ergeben sich beiderseits des Umlenkelements ringförmige Kanäle für das Arbeitsmedium. Weiter bevorzugt ist das ringförmige Umlenkelement näherungsweise allseitig von Arbeitsmedium umströmbar angeordnet. Weiter bevorzugt weist das ringförmige Umlenkelement zumindest abschnittsweise eine tropfen-, halb- mond- oder tragf lügeiförmige Querschnittsgeometrie auf. Hierdurch erfolgt eine vorteilhafte Umlenkung des Arbeitsmediums im Bereich des Laufrads. Damit wird ein besonders effizienter Betrieb der Strömungsvorrichtung ermöglicht. According to a further embodiment of the invention, the deflecting element comprises a side facing the impeller and a side facing away from the impeller. The deflecting element is here positioned such that it can be flowed around on both sides of the working medium. Accordingly arise on both sides of the deflecting annular channels for the working fluid. More preferably, the annular deflecting element is arranged approximately on all sides by working medium umströmbar. More preferably, the annular deflecting element at least in sections on a drop, semi-moon or Tragf liege-shaped cross-sectional geometry. This results in an advantageous deflection of the working medium in the region of the impeller. This enables a particularly efficient operation of the flow device.
In einer weiteren Ausgestaltung der Erfindung weist der Leitkörper mehrere voneinander beabstandete Umlenkelemente auf, die zusammen ein durchströmbares Gitter mit ringförmigen Kanälen bilden. Damit wird der Gesamtstrom des Arbeitsmediums in mehrere ringförmige Teilströme unterteilt. Innerhalb eines solchen Gitters aus Umlenkelementen kann der Gesamtstrom wirksam umgelenkt werden, wobei die gebildeten einzelnen Teilströme un- terschiedlichen Behandlungen unterzogen werden können, indem die Konturen der Umlenkelemente voneinander unterschiedlich gestaltet werden. Auf den Umlenkelementen können wiederum weitere Strömungsleitelemente wie Turbulenzpromotoren, Oberflächenbeschichtungen oder dergleichen angeordnet sein. Derselbe Effekt kann grundsätzlich auch bei Verwendung nur eines Umlenkelements erreicht werden. In a further embodiment of the invention, the guide body on a plurality of spaced deflecting elements, which together form a through-flow grating with annular channels. Thus, the total flow of the working medium is divided into a plurality of annular partial streams. Within such a grid of deflecting elements, the total current can be deflected effectively, wherein the individual partial flows formed can be subjected to different treatments by making the contours of the deflecting elements different from each other. In turn, further flow guidance elements such as turbulence promoters, surface coatings or the like can be arranged on the deflection elements. The same effect can basically be achieved even when using only one deflecting element.
In weiterer Ausgestaltung der Erfindung sind die voneinander beabstandeten Umlenkelemente derart positioniert, dass deren den Schaufeln des Laufrades zugewandte Kanten in axialer Richtung einen axialen Abstand aufwei- sen. Zugleich weisen die den Schaufeln des Laufrades zugewandte Kanten wenigstens näherungsweise den gleichen (Außen-)Durchmesser auf, der wiederum um maximal 10% kleiner ist als ein (gemeinsamer) Durchmesser der inneren Kanten der Laufradschaufeln. Somit wird eine nennenswerte Vereinigung der aus den Schaufelkanälen austretenden Teilströme des Ar- beitsmediums unterbunden. Vielmehr werden die in Umfangsrichtung des Laufrades separierten Teilströme im Leitkörper nochmals in (bezogen auf das Laufrad) axialer Richtung unterteilt. Dies kann selbstverständlich auch bei Verwendung nur eines Umlenkelements erreicht werden. In weiterer Ausgestaltung der Erfindung sind die voneinander beabstandeten Umlenkelemente derart positioniert, dass deren in Richtung der Rotationsachse des Laufrads weisenden Kanten einen unterschiedlichen radialen Ab- stand bezüglich der Rotationsachse des Laufrads aufweisen. Damit werden unterschiedliche Teilströme des Arbeitsmediums mit unterschiedlichem radialem Abstand in einen nachgeschalteten Diffusor entlassen und unerwünschte Verwirbelungen minimiert. In a further embodiment of the invention, the deflecting elements spaced from each other are positioned such that their edges facing the blades of the impeller have an axial spacing in the axial direction. At the same time, the edges facing the blades of the impeller at least approximately the same (outer) diameter, which in turn is smaller by a maximum of 10% than a (common) diameter of the inner edges of the impeller blades. Thus, a significant combination of emerging from the blade channels partial flows of the working medium is prevented. Rather, the separated in the circumferential direction of the impeller partial flows in the guide body are divided again in (relative to the impeller) axial direction. This can of course be achieved even when using only one deflecting element. In a further embodiment of the invention, the deflecting elements spaced apart from each other are positioned such that their edges pointing in the direction of the axis of rotation of the impeller have a different radial deflection. stand with respect to the axis of rotation of the impeller. Thus, different partial flows of the working medium are released with different radial distance in a downstream diffuser and minimized undesirable turbulence.
Nach einem weiteren Aspekt der Erfindung sind an einer mit dem Laufrad verbundenen Welle mehrere Permanentmagneten und/oder Rotorwicklungen angeordnet sind, die mit mehreren benachbart angeordneten, die Welle umgreifenden Statorwicklungen einen elektrischen Generator bilden. Dement- sprechend kann die Strömungsmaschine als„Generatorturbine" zur Stromerzeugung verwendet werden. According to a further aspect of the invention, a plurality of permanent magnets and / or rotor windings are arranged on a shaft connected to the impeller, which with a plurality of adjacently arranged, the shaft encircling stator windings form an electrical generator. Accordingly, the turbomachine can be used as a "generator turbine" for power generation.
Eine erfindungsgemäße Strömungsmaschine kann insbesondere eine thermische Strömungsmaschine sein. Eine Idee der Erfindung ist es darüber hin- aus, eine erfindungsgemäße Strömungsmaschine als Turbine, insbesondere als Radialturbine, in einem Organic-Rankine-Kreisprozess zu verwenden. A turbomachine according to the invention may in particular be a thermal turbomachine. An idea of the invention is, moreover, to use a turbomachine according to the invention as a turbine, in particular as a radial turbine, in an Organic Rankine cycle.
Die Erfindung erstreckt sich deshalb auch auf eine Anlage für das Umwandeln von Energie mit einem Kreisprozess, in der eine erfindungsgemäße Strömungsmaschine eingesetzt wird. Insbesondere betrifft die Erfindung eine Radialturbine für eine Anlage für das Umwandeln von Energie in Form einer sogenannten ORC-Anlage. Als ORC-Anlage wird dabei eine Anlage bezeichnet, in der ein thermodynamischer Kreisprozess in Form eines„Organic Rankine Cycle" (ORC) durchgeführt wird, mit dem Wärme in mechanische Energie gewandelt werden kann. The invention therefore also extends to a system for converting energy with a cyclic process in which a turbomachine according to the invention is used. In particular, the invention relates to a radial turbine for a plant for the conversion of energy in the form of a so-called ORC plant. An ORC plant is a plant in which a thermodynamic cycle in the form of an "Organic Rankine Cycle" (ORC) is performed, with which heat can be converted into mechanical energy.
Die einer erfindungsgemäßen ORC-Anlage zugeführte Wärme kann zum Beispiel aus einer Wärmequelle in Form einer Brennkraftmaschine aus einer Kraft-Wärme-Kopplungsanlage, aus einer Biomasse-Feuerungsanlage, aus einer Geothermie-Quelle oder aus einem Solarkraftwerk stammen. Mittels einer ORC-Anlage kann jede Form von Abwärme genutzt werden. Beispiels- weise kann aus der Abwärme von Verbrennungsmotoren mittels einer ORC- Anlage zusätzlich elektrische Energie gewonnen werden. The heat supplied to an ORC system according to the invention can originate, for example, from a heat source in the form of an internal combustion engine from a combined heat and power plant, from a biomass combustion plant, from a geothermal source or from a solar power plant. Any form of waste heat can be used with an ORC system. Beispiels- example can be obtained from the waste heat of internal combustion engines by means of an ORC plant additional electrical energy.
Eine erfindungsgemäße ORC-Anlage kann einen Kondensator zur Verflüssi- gung eines Arbeitsmediums der Anlage, eine Pumpe, einen Verdampfer zur Verdampfung des Arbeitsmediums enthalten. In einer solchen Anlage gibt es eine dem Verdampfer nachgeschalteten Strömungsmaschine, insbesondere eine Turbine, in der das Arbeitsmedium unter Entnahme von kinetischer Energie aus dem Kreislauf entspannt wird. An ORC plant according to the invention may contain a condenser for liquefying a working medium of the plant, a pump, an evaporator for evaporating the working medium. In such a plant, there is a turbomachine downstream of the evaporator, in particular a turbine, in which the working fluid is expanded while removing kinetic energy from the circulation.
Die Pumpe bringt ein bei Normbedingungen flüssiges Arbeitsmedium auf Betriebsdruck. Nachfolgend durchströmt das noch flüssige Arbeitsmedium den Wärmetauscher (Verdampfer) oder auch ein Wärmetauschersystem, in dem thermische Energie beispielsweise aus einer der vorgenannten Quellen auf das Arbeitsmedium der ORC-Anlage übertragen wird. Durch den Energieeintrag verdampft das Arbeitsmedium bevorzugt vollständig. Am Austritt des Verdampfers entsteht dann Sattdampf bzw. Trockendampf. Durch den Energieeintrag im Verdampfer nehmen das spezifische Volumen und die Temperatur des Dampfes zu. The pump brings a liquid working under standard conditions to operating pressure. Subsequently, the still liquid working medium flows through the heat exchanger (evaporator) or a heat exchanger system in which thermal energy is transferred for example from one of the aforementioned sources to the working medium of the ORC system. Due to the energy input, the working medium preferably evaporates completely. At the outlet of the evaporator then saturated steam or dry steam is formed. The energy input in the evaporator increases the specific volume and the temperature of the steam.
Der Dampf des Arbeitsmediums wird über eine erfindungsgemäße Strömungsvorrichtung in Form einer Turbine nahezu isentrop auf einen geringeren Druck entspannt. Das spezifische Volumen nimmt dann durch die Expansion in der Turbine zu. Diese Volumenvergrößerung, hervorgerufen durch die Druckdifferenz und die daraus resultierende Arbeit, wird als Volumenänderungsarbeit bezeichnet, welche die Turbine an ihren Schaufeln in mechanische Energie umwandelt. The vapor of the working medium is expanded almost isentropically to a lower pressure via a flow device according to the invention in the form of a turbine. The specific volume then increases due to the expansion in the turbine. This increase in volume, caused by the pressure difference and the resulting work, is called volume change work, which converts the turbine on their blades into mechanical energy.
Aus der Turbine strömt der Dampf gegebenenfalls durch einen Regenerator, in dem ein Wärmeaustausch zwischen dem dampfförmigen Arbeitsmedium und dem von der Pumpe kommenden flüssigen Arbeitsmedium stattfindet (innerer Wärmeaustausch). Das in der Turbine und ggf. im Regenerator auf Kondensationstemperatur gebrachte (noch dampfförmige) Arbeitsmedium gelangt in den nachgeschalteten Kondensator, in dem das Arbeitsmedium unter Abgabe von Niedertem- peraturwärme rekondensiert wird. Die bei der Kondensation abgegebene Wärme wird bevorzugt noch über einen Kühlwasserkreislauf in ein Wärmenetz gespeist. Das Arbeitsmedium kondensiert aus und geht wieder vollständig in den flüssigen Aggregatzustand über. Die Speisepumpe (Pumpe) bringt nachfolgend das Arbeitsmedium auf Betriebsdruck und anschließend wieder in den Verdampfer. Damit schließt sich der Kreislauf. If necessary, the steam flows out of the turbine through a regenerator in which a heat exchange takes place between the vaporous working medium and the liquid working medium coming from the pump (internal heat exchange). The (still vaporous) working medium brought to the condensation temperature in the turbine and possibly in the regenerator reaches the downstream condenser, in which the working medium is recondensed with the release of low-temperature heat. The heat released in the condensation is preferably fed via a cooling water circuit in a heat network. The working medium condenses out and returns completely to the liquid state of aggregation. The feed pump (pump) subsequently brings the working fluid to operating pressure and then back into the evaporator. This completes the cycle.
Mit einer als Turbine in einer ORC-Anlage eingesetzten erfindungsgemäßen Strömungsvorrichtung kann insbesondere ein Generator angetrieben werden, der mit der Turbine aus thermischer Energie gewonnenen mechani- sehen Energie elektrischen Strom erzeugt. With a flow device according to the invention used as a turbine in an ORC system, in particular a generator can be driven, which generates electrical current with the mechanical energy generated by the turbine from thermal energy.
Eine solche ORC-Anlage mit einer erfindungsgemäßen Strömungsmaschine (Turbine) kann sowohl für kleine und große Hausanlagen als auch für große industrielle Anlagen sowie für Kraftwerke eingesetzt werden. Als Hausanla- gen sind dabei die Energieversorgungen, z. B. Klimatisierungsanlagen für Büros, Garagen, Krankenhäuser und alle Arten von Gebäuden zu verstehen. Industrielle Anlagen sind z.B. Fertigungsanlagen, insbesondere Fertigungsanlagen der Automobilindustrie, insbesondere Lackierereien, in denen ein ausgewogener Bedarf an Strom (aus mechanischer Energie) und Wärme auf unterschiedlichem Temperaturniveau benötigt wird. Such an ORC system with a turbomachine according to the invention can be used both for small and large domestic installations as well as for large industrial plants and power plants. As house equipment are the power supplies, z. As air conditioning systems for offices, garages, hospitals and all types of buildings to understand. Industrial plants are e.g. Manufacturing plants, in particular manufacturing plants of the automotive industry, in particular paint shops, in which a balanced demand for electricity (from mechanical energy) and heat at different temperature levels is needed.
Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung mehrerer bevorzugter Ausführungsbeispiele sowie anhand der Zeichnungen. Further advantages, features and details of the invention will become apparent from the following description of several preferred embodiments and from the drawings.
Die vorstehend in der Beschreibung genannten Merkmale und Merkmalskombinationen sowie die nachfolgenden in der Figurenbeschreibung genann- ten und/oder in den Figuren alleine gezeigten Merkmale und Merkmalskombinationen sind nicht nur in der jeweils angegeben Kombination, sondern auch in anderen Kombinationen oder in Alleinstellung verwendbar, ohne den Rahmen der Erfindung zu verlassen. The features and feature combinations mentioned above in the description as well as the subsequent features mentioned in the description of the figures. th and / or alone shown in the figures features and combinations of features can be used not only in the specified combination, but also in other combinations or alone, without departing from the scope of the invention.
Vorteilhafte Ausführungsformen einer erfindungsgemäßen Strömungsmaschine sind in der Fig. 2, Fig. 3, Fig. 4. Fig. 5a und Fig. 5b dargestellt und werden nachfolgend beschrieben. Es zeigen: Advantageous embodiments of a turbomachine according to the invention are shown in FIGS. 2, 3, 4, 5 a and 5b and will be described below. Show it:
Fig. 2 eine Schnittansicht einer Radialturbine für Überschallströmung mit einem Umlenkelement in Form eines Rotationshyperboloiden (Laufradkegel) zur Umlenkung der Strömung innerhalb des Laufrads; 2 shows a sectional view of a radial turbine for supersonic flow with a deflecting element in the form of a hyperboloid of revolution (impeller cone) for deflecting the flow within the impeller;
Fig. 3 eine Schnittansicht eines Laufrads einer Radialturbine für Überschallströmung mit einem abschnittsweise in das Laufrad hineinragenden Leitkörper zur Verringerung der Wirbelbildung in einem nachgeschalteten Diffusor; 3 is a sectional view of an impeller of a radial turbine for supersonic flow with a sectionally projecting into the impeller guide body for reducing the vortex formation in a downstream diffuser.
Fig. 4 eine Schnittansicht einer Strömungsvorrichtung mit hauptsächlich innerhalb des Laufrads liegenden Leitkörpern; 4 shows a sectional view of a flow device with guide bodies located mainly within the rotor wheel;
Fig. 5a in einer vergrößerten Schnittansicht einen Abschnitt der Strömungs- Vorrichtung nach Fig. 4; und eine Ansicht von Schaufeln des Laufrads der erfindungsgemäßen Strömungsvorrichtung aus Fig. 5a, die zur Verdeutlichung ihrer Geometrie quer zur Schaufelachse geschnitten gezeigt sind. Fig. 5a is an enlarged sectional view of a portion of the flow device of Fig. 4; and Fig. 5a shows a view of vanes of the impeller of the flow device according to the invention from Fig. 5a, which are shown cut to illustrate their geometry transversely to the blade axis.
Fig. 2 zeigt abschnittsweise eine Schnittansicht einer erfindungsgemäßen Strömungsmaschine in Form einer Radialturbine mit einem im Wesentlichen ruhenden Turbinengehäuse 1 , 4, 1 1 , in dem ein Turbinenrad 2 (Laufrad) angeordnet ist. Das Turbinengehäuse 1 , 4, 1 1 umfasst insbesondere einen Düsenring 1 sowie eine zugehörige Abdeckung 1 1 . Die Abdeckung 1 1 und der Düsenring 1 sind bevorzugt als separate Baugruppen ausgeführt. Zwischen ihnen sind die Düsenkanäle 10 gebildet. Das Turbinengehäuse 1 , 4, 1 1 umfasst einen Diffusor 4 mit einem Austrittkanal 40 für das Arbeitsmedium. Fig. 2 shows a section of a sectional view of a turbomachine according to the invention in the form of a radial turbine with a substantially stationary turbine housing 1, 4, 1 1, in which a turbine wheel 2 (impeller) is arranged. The turbine housing 1, 4, 1 1 comprises in particular a nozzle ring 1 and an associated cover 1 1. The cover 1 1 and the nozzle ring 1 are preferably designed as separate modules. Between them, the nozzle channels 10 are formed. The turbine housing 1, 4, 1 1 comprises a diffuser 4 with an outlet channel 40 for the working medium.
Das in dem Turbinengehäuse angeordnete Laufrad 2 umfasst eine Mehrzahl von (mitrotierenden) Schaufeln. In der Fig. 2 ist das Laufrad 2 mit einer Schaufel 21 gezeigt. Zwischen den Schaufeln des Laufrades 2 sind gerade oder gekrümmte Schaufelkanäle 20 ausgebildet, die einen im Wesentlichen rechteckigem Querschnitt haben. Die Schaufeln sind über eine Basis des Laufrades 2 sowie auf einer davon beabstandeten Seite über eine sogenannte Bandage 22 miteinander verbunden. The impeller 2 disposed in the turbine housing includes a plurality of (co-rotating) vanes. In FIG. 2, the impeller 2 is shown with a blade 21. Between the blades of the impeller 2 straight or curved blade channels 20 are formed, which have a substantially rectangular cross-section. The blades are connected to each other via a base of the impeller 2 and on a side spaced therefrom via a so-called bandage 22.
Ein dampfförmiges Arbeitsmedium, beispielsweise das Arbeitsmedium einer ORC-Anlage, strömt durch einen als Einströmungskanal wirkenden Düsenkanal 10 des Turbinengehäuses 1 1 gemäß eines Richtungspfeils 51 . In dem Einströmungskanal 10 wird über eine entsprechende Düsengeometrie das strömende Arbeitsmedium beschleunigt, so dass an einer Engstelle Schallgeschwindigkeit erreicht, wobei das Arbeitsmedium vor einer Überleitung in das Laufrad 2 auf Überschallgeschwindigkeit gebracht werden kann. A vaporous working medium, for example the working medium of an ORC system, flows through a nozzle channel 10 of the turbine housing 1 1 acting as an inflow channel in accordance with a directional arrow 51. In the inflow passage 10, the flowing working medium is accelerated via a corresponding nozzle geometry, so that sound velocity is reached at a constriction, wherein the working medium can be brought to supersonic speed before being transferred to the impeller 2.
Das dampfförmige Arbeitsmedium strömt aus dem Düsenkanal 10 und trifft auf die Schaufel 21 , die derart ausgebildet ist, dass sowohl die angeströmte Kante als auch die in Abströmungsrichtung liegende Kante der Schaufel 21 und somit auch diese selbst parallel und axial zur Laufradwelle ausgerichtet sind. Der überwiegende Teil des Stromes 51 an Arbeitsmedium wird nach dem Passieren der Schaufeln 21 bzw. eines jeweiligen Schaufelkanals zwi- sehen mehreren Schaufeln 21 (und somit in einem sogenannten Zwischenbereich des Laufrades 2) auf Parallelität zur Rotationsachse des Laufrades umgelenkt (Pfeilrichtung 53). Hierzu ist erfindungsgemäß ein Leitkörper 3 in Form eines kegeligen Umlenkelements (Laufradkegel) vorgesehen, der bevorzugt als Rotationshyperboloid gestaltet ist. Dieses Umlenkelement kann optional einstückig mit dem Laufrad ausgeführt sein kann. Der Leitkörper 3 befindet sich in einem Zwischenbereich 29 zwischen dem Schaufelkanalaus- tritten 23 und der Eintrittsöffnung 24 in den von dem Diffusor 4 gebildeten Austrittskanal 40. Das als Laufradkegel ausgebildete Umlenkelement mit dem Leitkörper 3 ist dabei im Bereich seiner Basis in dem Zwischenbereich 29 innerhalb des Laufrades 2 angeordnet. Er wird abschnittsweise ringförmig von den Schaufelkanalaustritten 23 bzw. von den Schaufeln 21 des Laufra- des umschlossen. Der Leitkörper 3 erstreckt sich in den von dem Diffusor 4 gebildeten Austrittskanal 40. The vaporous working medium flows out of the nozzle channel 10 and impinges on the blade 21, which is designed in such a way that both the flowed edge and the downstream edge of the blade 21 and therefore also these are aligned parallel to and axially towards the impeller shaft. The majority of the stream 51 of working medium is after passing through the blades 21 or a respective blade channel between see several blades 21 (and thus in a so-called intermediate region of the impeller 2) deflected parallelism to the axis of rotation of the impeller (arrow 53). For this purpose, according to the invention a guide body 3 in Form of a conical deflecting element (impeller cone) provided, which is preferably designed as a rotational hyperboloid. This deflecting element can optionally be designed in one piece with the impeller. The guide body 3 is located in an intermediate region 29 between the blade channel outlet 23 and the inlet opening 24 in the outlet channel 40 formed by the diffuser 4. The deflecting element with the guide body 3 designed as an impeller cone is in the region of its base in the intermediate region 29 within the Impeller 2 arranged. It is enclosed in sections annularly by the blade channel outlets 23 and by the blades 21 of the rotor. The guide body 3 extends into the outlet channel 40 formed by the diffuser 4.
Der Laufradkegel bewirkt bei moderaten Strömungsgeschwindigkeiten eine weitgehend laminare Strömungsumlenkung. Bei hohen Strömungsgeschwin- digkeiten können Wirbel 54 entstehen. The impeller cone causes a largely laminar flow deflection at moderate flow velocities. At high flow velocities, vortices 54 can occur.
Zur Verminderung des in Fig. 2 dargestellten Wirbelbildungseffektes kann durch die Positionierung von Leitkörpern in dem Abströmkanal bzw. in dem Diffusor 4 hinter dem Laufrad 2 eine Reduzierung der Wirbelbildung erzielt werden. In order to reduce the vortex formation effect shown in FIG. 2, the positioning of guide bodies in the outflow channel or in the diffuser 4 behind the impeller 2 can reduce vortex formation.
Eine weitere erfindungsgemäße Strömungsvorrichtung ist in der Fig. 3 dargestellt, die im Wesentlichen gleichartig wie die Strömungsvorrichtung gemäß Fig. 2 ausgeführt ist. Entsprechend kann auf die vorstehende Beschrei- bung zu Fig. 2 Bezug genommen werden. Entsprechend sind auch gleichartige Bauelemente und Funktionseinheiten mit gleichen Bezugszeichen versehen. Die Strömungsvorrichtung nach Fig. 3 umfasst neben einem ersten Umlenkelement in Form des mitrotierenden Laufradkegels ein zweites Umlenkelement 31 in Form eines gehäuseseitig montierten, ringförmigen Leit- körpers 3\ Der Leitkörper 3' greift bevorzugt in einen Zwischenbereich 29 des Laufrads 2 ein, der von den Laufradschaufeln 21 umgriffen wird. Dadurch kann der aus den Laufradschaufelkanälen austretende Strom Arbeitsmedium frühzeitig in zwei ringförmige Teilströme aufgeteilt werden. A further flow device according to the invention is shown in FIG. 3, which is essentially the same as the flow device according to FIG. 2. Accordingly, reference can be made to the above description to Fig. 2 reference. Accordingly, similar components and functional units are provided with the same reference numerals. The flow apparatus according to FIG. 3 comprises, in addition to a first deflection element in the form of the co-rotating impeller cone, a second deflection element 31 in the form of a ring-shaped guide body 3 mounted on the housing side. The guide body 3 ' preferably engages in an intermediate region 29 of the impeller 2, which differs from the one Impeller blades 21 is encompassed. As a result, the stream of working fluid emerging from the impeller blade channels can be split early into two annular partial streams.
Der Leitkörper 3' weist eine erste und eine zweite ringförmige Kante 25, 26 auf. Die erste Kante 25 des Umlenkelements ist benachbart zu dem Schaufelkanalaustritt 23 innerhalb des Zwischenbereichs 29 positioniert. Die zweite Kante 26 ist benachbart zu der Eintrittsöffnung 24 innerhalb des Austrittskanals 40 angeordnet. Die die erste Kante 25 wirkt dabei als eine Anströmkante. Die zweite Kante 26 ist eine Abströmkante. Das Umlenkelement 31 ist mit einer Leitkontur 28 ausgebildet, die sich von der ersten Kante 25 aus einer näherungsweise zu einer Rotationsachse 27 des Laufrades 2 radialen Richtung zu der zweiten Kante 26 in eine näherungsweise zu der Rotationsachse 27 des Laufrades 2 axiale Richtung erstreckt. Das aus dem Schaufelkanal 20 ausströmende Arbeitsmedium wird damit von dem Umlenkelement 31 aus einer im Wesentlichen radialen in eine im wesentlichen axiale Richtung umgelenkt. In modifizierten Ausführungsbeispielen können auch andere Strömungsrichtungen erzeugt werden, indem die Konturen der Umlenkelemente in die entsprechenden Richtungen orientiert werden. The guide body 3 ' has a first and a second annular edge 25, 26. The first edge 25 of the deflection element is positioned adjacent to the blade channel exit 23 within the intermediate region 29. The second edge 26 is arranged adjacent to the inlet opening 24 within the outlet channel 40. The first edge 25 acts as a leading edge. The second edge 26 is a trailing edge. The deflecting element 31 is formed with a guide contour 28, which extends from the first edge 25 from an approximately to a rotational axis 27 of the impeller 2 radial direction to the second edge 26 in an approximately to the axis of rotation 27 of the impeller 2 axial direction. The effluent from the blade channel 20 working fluid is thus deflected by the deflecting element 31 from a substantially radial in a substantially axial direction. In modified embodiments, other flow directions can be generated by the contours of the deflecting elements are oriented in the corresponding directions.
Falls trotz der beschriebenen Maßnahmen Restwirbel 54 entstehen - beispielsweise bei besonders hohen Strömungsgeschwindigkeiten können erfindungsgemäß alternativ oder zusätzlich weitere Verbesserungen vorgesehen werden. Insbesondere werden in ORC-Anlagen häufig Radialturbinen zur Umwandlung der Strömungsenergie des Arbeitsmediums in ein Drehmoment verwendet. Aufgrund der niedrigen Schallgeschwindigkeit in solchen Medien und der hohen Druckverhältnisse zwischen Ein- und Austritt des Dampfes in die Turbine liegt die Strömungsgeschwindigkeit des Dampfes im Laufrad der Turbi- ne häufig oberhalb der Schallgeschwindigkeit. Auch die Austrittsgeschwindigkeit des Dampfes aus dem Laufrad liegt häufig noch über Mach 0,7. Unter Betrachtung des geometrisch vorgegebenen großen Unterschieds zwischen dem Krümmungsradius des Laufradkegels und der inneren Kante einer Bandage 22 über den Schaufeln 21 sowie durch die hohe Abströmgeschwindigkeit wird ein gleichmäßiges Abströmen des dampfförmigen Arbeitsmediums in Turbinen von ORC-Anlagen häufig verhindert. If residual vortices 54 occur in spite of the measures described-for example, at particularly high flow velocities, further or further improvements may be provided according to the invention as an alternative or in addition. In particular, radial turbines are often used in ORC plants for converting the flow energy of the working medium into a torque. Due to the low sound velocity in such media and the high pressure ratios between the inlet and outlet of the steam in the turbine, the flow velocity of the steam in the impeller of the turbine is often above the speed of sound. Also, the exit velocity of the steam from the impeller is often still over Mach 0.7. Considering the geometrically given big difference between the radius of curvature of the impeller cone and the inner edge of a bandage 22 over the blades 21 and by the high outflow velocity, a uniform outflow of the vaporous working medium in turbines of ORC systems is often prevented.
In den Fig. 4, 5a und 5b sind Ausschnitte einer weiteren erfindungsgemäßen, als Radialturbine ausgebildeten Strömungsmaschine gezeigt, die einen Düsenring 1 mit einer Düsenabdeckung 1 1 , ein in einem Gehäuse auf einer Welle gelagerten Laufrad 2, einen Einströmungskanal 10, einen Diffusor 4, mehrere am Laufrad 2 angeordnete Schaufeln 21 , einen ersten gitterförmi- gen Leitkörper 3" und einen zweiten kegeligen Leitkörper 3 aufweist. Eine grundsätzliche Funktionsweise entspricht derjenigen der Radialturbine nach Fig. 2 bzw. Fig. 3, so dass auf die hierzu gemachten Ausführungen Bezug genommen werden kann. 4, 5a and 5b are sections of a further inventive, designed as a radial turbine flow machine shown, the nozzle ring 1 with a nozzle cover 1 1, mounted in a housing on a shaft impeller 2, an inflow passage 10, a diffuser 4, a plurality of blades arranged on the impeller 2, a first lattice-shaped guide body 3 " and a second conical guide body 3. A basic mode of operation corresponds to that of the radial turbine according to Fig. 2 or Fig. 3, so that reference is made to the statements made for this purpose can be.
Ein dampfförmiges Arbeitsmedium ist über den Einströmungskanal 10 zu einem Radeintritt des Laufrads gemäß eines Richtungspfeils 51 leitbar. Es trifft dort auf die Schaufel 21 und strömt zwischen den Schaufeln 21 in einen Schaufelkanal 20 gemäß eines Richtungspfeils 42 ein (Fig. 5b). Die Anströ- mung auf die Schaufel 21 erfolgt in radialer Richtung bezüglich einer Rotationsachse des Laufrads 2. Nach Durchströmung des Schaufelkanals 20 gelangt das Arbeitsmedium in einen Zwischenbereich 29 zwischen einem Schaufelkanalaustritt und einem dem Laufrad 2 nachgeschalteten Austrittskanal 40. In dem Zwischenbereich 29 nach dem Schaufelkanalaustritt und einem Diffusorkanaleintritt sind erfindungsgemäß der erste Leitkörper 3" und der zweite Leitkörper 3 positioniert, wobei beide Leitkörper bevorzugt auch abschnittsweise aus dem Zwischenbereich heraus in den Austrittskanal 40 ragen können. Gemäß der Fig. 5a umfasst der erste Leitkörper 3" neben einem ebenfalls gitterförmigen, insbesondere mit radialen Speichen versehenen, durchströmbaren Befestigungsring 34 zwei kreisringförmige Umlenkelemente 31 und 32, wobei in alternativen Ausführungsbeispielen mehr als zwei Umlenkelemente verwendbar sind. Alternativ kann auch ein einzelnes kreisringförmiges Umlenkelement 31 vorgesehen sein. Die kreisringförmigen Umlenkelemente 31 , 32 sind bevorzugt zusammen mit dem Befestigungsring 34 einstückig ausge- führt und bilden so den ersten Leitkörper 3", der auch als Strömungsgitter bezeichnet werden kann. Der so aufgebaute erste Leitkörper 3" wirkt mit dem zweiten Leitkörper 3 in Form des Laufradkegels zusammen: Beide Leitkörper 3, 3" teilen zusammenwirkend den Zwischenbereich 29 des Laufrads 2 zumindest abschnittsweise in voneinander separierte ringförmige Strö- mungskanäle auf. A vaporous working medium can be conducted via the inflow passage 10 to a wheel entry of the impeller according to a directional arrow 51. It hits the blade 21 there and flows between the blades 21 into a blade channel 20 according to a directional arrow 42 (FIG. 5b). The flow onto the blade 21 takes place in the radial direction with respect to a rotational axis of the impeller 2. After flowing through the blade channel 20, the working fluid passes into an intermediate region 29 between a blade channel outlet and an outlet channel 40 downstream of the rotor 2. In the intermediate region 29 after the blade channel outlet and a diffuser channel entrance, according to the invention, the first guide body 3 " and the second guide body 3 are positioned, whereby both guide bodies can preferably extend in sections out of the intermediate area into the outlet channel 40. According to FIG. 5a, the first guide body 3 " also comprises a lattice-shaped, in particular provided with radial spokes, permeable mounting ring 34 two annular deflecting elements 31 and 32, wherein in alternative embodiments, more than two deflecting elements are usable. Alternatively, a single annular deflecting element 31 may also be provided. The annular deflection elements 31, 32 are preferably carried integrally excluded together with the mounting ring 34 and thus form the first guide body 3 ", which may also be referred to as a flow grid. The thus constructed first guide member 3 'engages with the second guide member 3 in the form of Impeller cone together: both guide body 3, 3 " cooperatively share the intermediate region 29 of the impeller 2 at least in sections into separate annular flow channels.
Das Arbeitsmedium wird unmittelbar nach den Schaufeln 21 durch die Umlenkelemente 31 und 32 des ersten Leitkörpers 3" dementsprechend mehrfach aufgeteilt und zum überwiegenden Teil noch innerhalb des Schaufelra- des 2 parallel zu dessen Rotationsachse gemäß eines Richtungspfeils 53 gelenkt. The working medium is accordingly divided several times immediately after the blades 21 by the deflecting elements 31 and 32 of the first guide body 3 " and for the most part still directed within the blade wheel 2 parallel to its axis of rotation according to a directional arrow 53.
Der erste Leitkörper 3" erstreckt sich zwischen einer ersten 25 und einer zweiten Kante 26 eines Umlenkelements 31 bzw. 32 und ist derart ausgebil- det ist, dass die erste Kante benachbart zum Schaufelkanalaustritt positioniert ist, wobei die zweite Kante 26 benachbart zum Diffusorkanaleintritt 40 positioniert ist. The first guide body 3 " extends between a first 25 and a second edge 26 of a deflection element 31 or 32 and is designed such that the first edge is positioned adjacent to the blade channel exit, wherein the second edge 26 is positioned adjacent to the diffuser channel entrance 40 is.
Das Umlenkelement 31 , 32 ist derart ausgebildet, dass die erste Kante 25 als Anströmkante dient und in radialer Richtung zur Rotationsachse des Laufrades 2 weist, wobei die zweite Kante 26 eine Abströmkante ist und in die gleiche Richtung wie die Rotationsachse weist, so dass das aus dem Schaufelkanal 20 ausströmende Arbeitsmedium von einer radialen in eine näherungsweise axiale Richtung umgelenkt wird. Dabei weisen beide Umlen- kelemente 31 , 32 jeweils eine dem Laufrad 2 zugewandte und eine dem Laufrad 2 abgewandte Seite auf. Die Umlenkelemente 31 , 32 sind insbeson- dere derart positioniert, dass sie vom Arbeitsmedium beidseitig umströmbar sind. The deflection element 31, 32 is formed such that the first edge 25 serves as leading edge and in the radial direction to the axis of rotation of the impeller 2, wherein the second edge 26 is a trailing edge and facing in the same direction as the axis of rotation, so that from the working fluid flowing from the blade channel 20 is deflected from a radial to an approximately axial direction. Both deflecting elements 31, 32 each have a side facing the impeller 2 and a side facing away from the impeller 2. The deflecting elements 31, 32 are in particular so positioned that they are flow around the working medium on both sides.
Infolgedessen wird das Arbeitsmedium nach dessen Austritt aus dem Schau- felkanal 20 derart in den Diffusorkanal 40 umgelenkt, dass ein Entlangströmen am Laufrad 2 optimiert wird. As a result, the working medium is deflected after its exit from the bluff channel 20 in such a way in the diffuser channel 40 that a flow along the impeller 2 is optimized.
Die Umlenkelemente 31 und 32 des ersten Leitkörpers 3" weisen bevorzugt halbmondförmige Querschnittskonturen auf, wobei deren Profil strömungs- günstig ausgestaltet ist. Die zum Laufrad 2 weisende erste Kante (ringförmige Anströmkante) weist radial vom Zentrum weg. Die auf der axialen Gegenseite befindliche zweite Kante (ringförmige Abströmkante) weist von der Laufradbasis 2 weg. Die Krümmung des Profils der Umlenkelemente ist so gestaltet, dass das Arbeitsmedium kontinuierlich parallel zur Rotationsachse des Laufrads 2 umgelenkt wird. The deflecting elements 31 and 32 of the first guide body 3 " preferably have crescent-shaped cross-sectional contours, the profile of which has a favorable flow configuration. The first edge (annular leading edge) pointing towards the impeller 2 points radially away from the center The second edge located on the axial opposite side (annular trailing edge) points away from the impeller base 2. The curvature of the profile of the deflecting elements is designed so that the working medium is continuously deflected parallel to the axis of rotation of the impeller 2.
Werden bei dem Leitkörper 3" mehrere ringförmige Umlenkelemente 31 , 32 verwendet, so weisen die Abströmkanten dieser Umlenkelemente 31 , 32 unterschiedliche Durchmesser bezüglich der Rotationsachse des Laufrads 2 auf, während es zweckmäßig ist, dass die Anströmkanten den gleichen Durchmesser bezüglich einer Rotationsachse des Laufrads 2 besitzen. Vorzugsweise sind die Anströmkanten möglichst dicht an den Austrittskanten der Schaufeln 21 positioniert. Hierzu ist es sinnvoll, dass die (im Wesentlichen gleichen) Durchmesser der Anströmkanten der Umlenkelemente 31 , 32 ei- nen Durchmesser aufweisen, der weniger als 10% kleiner ist als der Durchmesser desjenigen Kreises, den alle Austrittskanten der Schaufeln berühren. If a plurality of annular deflecting elements 31, 32 are used in the guide body 3 " , then the trailing edges of these deflecting elements 31, 32 have different diameters with respect to the axis of rotation of the impeller 2, while it is expedient that the leading edges have the same diameter with respect to a rotational axis of the impeller 2 Preferably, the leading edges are positioned as close as possible to the exit edges of the blades 21. For this purpose, it makes sense that the (substantially equal) diameter of the leading edges of the deflecting elements 31, 32 have a diameter which is less than 10% smaller than the diameter of the circle touching all the exit edges of the blades.
Gemäß Fig. 5a weist jede Schaufel 21 am Schaufelkanalaustritt innerhalb des Laufrads 2 eine Schaufelhöhe 60 auf. Ein erster axialer Abstand 61 zwi- sehen einer Oberfläche der Laufradbasis und der Anström kante des (ersten) Umlenkelements 31 ist dabei kleiner als ein axialer Abstand zwischen der Anströmkante des (zweiten) Umlenkelements 32 und derselben Oberfläche der Laufradbasis, so dass zwischen den Anströmkanten beider Umlenkelemente 31 , 32 ein axialer Abstand 62 vorhanden ist. Außerdem ist die Anströmkante des Umlenkelements 32 zur Bandage 22 durch einen axialen Abstand 63 beabstandet angeordnet. According to FIG. 5 a, each blade 21 has a blade height 60 at the blade channel outlet within the rotor 2. A first axial distance 61 between see a surface of the impeller base and the inflow edge of the (first) deflecting element 31 is smaller than an axial distance between the leading edge of the (second) deflecting element 32 and the same surface the impeller base, so that between the leading edges of both deflecting elements 31, 32 an axial distance 62 is present. In addition, the leading edge of the deflecting element 32 to the drum 22 is spaced by an axial distance 63.
Ferner sind die zueinander benachbarten Umlenkelemente 31 ,32 derart positioniert, dass deren Abströmkanten 26 einen unterschiedlichen radialen Abstand bezüglich der Rotationsachse des Laufrads 2 aufweisen. Außerdem weisen die zu den Schaufeln des Laufrades weisenden Anströmkanten in axialer Richtung einen unterschiedlich axialen Abstand 61 bzw. Abstand 61 +62 zur Laufradbasis auf. Furthermore, the mutually adjacent deflecting elements 31, 32 are positioned such that their trailing edges 26 have a different radial distance with respect to the axis of rotation of the impeller 2. In addition, the leading edges facing the blades of the impeller have a different axial distance 61 or distance 61 +62 to the impeller base in the axial direction.
Das Laufrad 2 ist der rotierende Teil der Strömungsmaschine bzw. der Radialturbine, der dem strömenden Arbeitsmedium entweder Arbeit entzieht bei Verwendung der Strömungsmaschine als Turbine oder Arbeit zuführt bei Verwendung der Strömungsmaschine als Verdichter. Das Laufrad 2 ist mit einer nicht dargestellten Welle verbunden, über die erzeugte mechanische Energie abgeführt wird. In dem Leitkörper 3 nachgeschalteten Diffusor 4 wird durch Erweiterung des Strömungsquerschnitts die Gasströmung verlangsamt und der statische Gasdruck erhöht. Der Diffusor 4 stellt im Prinzip die Umkehrung einer Düse dar. The impeller 2 is the rotating part of the turbomachine or the radial turbine, which either extracts work from the flowing working medium when using the turbomachine as a turbine or work feeds when using the turbomachine as a compressor. The impeller 2 is connected to a shaft, not shown, is discharged through the generated mechanical energy. In the guide body 3 downstream diffuser 4 is slowed by expansion of the flow cross section, the gas flow and increases the static gas pressure. The diffuser 4 represents in principle the inversion of a nozzle.
Eine in Fig. 5a gezeigte Bandage 22 ist an den Schaufeln 21 angeordnet und dient dazu, das Laufrad 2 zu stabilisieren und in Form zu halten. A bandage 22 shown in Fig. 5a is arranged on the blades 21 and serves to stabilize the impeller 2 and to keep it in shape.
Der Leitkörper 3 bzw. die Umlenkelemente 31 bzw. 32 werden über Stege 33 vorzugsweise mit dem Turbinengehäuse oder dem Diffusor 4 der Turbine verbunden, so dass die aufgrund der Umlenkung des Arbeitsmediums wir- kenden Kräfte nicht auf die Laufradwelle übertragen werden. Der Leitkörper 3 ist das Gegenstück zum bewegten Laufrad 2, wobei der Leitkörper 3 vorzugsweise fest mit dem Gehäuse bzw. am Diffusor 4 über die Stege 33 aus- gebildet ist. Demnach bilden das Laufrad 2 und der Leitkörper 3 zusammen eine Stufe. Zur Befestigung der Umlenkelemente am Diffusor 4 ist ein Befestigungsring 34 des Leitkörpers 3 am Diffusoreinlauf vorgesehen. Es ist auch möglich, die Umlenkelemente 31 bzw. 32 an dem Laufrad 2 zu befestigen, so dass diese dann mitrotieren. Alternativ kann ein Umlenkelement am Laufrad und ein anderes am Gehäuse festgelegt sein. The guide body 3 or the deflecting elements 31 and 32 are preferably connected via webs 33 to the turbine housing or the diffuser 4 of the turbine, so that the forces acting on account of the diversion of the working medium are not transmitted to the impeller shaft. The guide body 3 is the counterpart to the moving impeller 2, wherein the guide body 3 preferably fixed to the housing or on the diffuser 4 via the webs 33 is formed. Accordingly, the impeller 2 and the guide body 3 together form a step. For fixing the deflecting elements on the diffuser 4, a fastening ring 34 of the guide body 3 is provided on the diffuser inlet. It is also possible to attach the deflecting elements 31 and 32 to the impeller 2, so that they then co-rotate. Alternatively, a deflecting element may be fixed to the impeller and another to the housing.
Der Leitkörper 3" bzw. die Umlenkelemente 31 bzw. 32 in einer erfindungs- gemäßen Strömungsmaschine sind aus einem (Edel-)Stahl hergestellt und werden mit zerspanenden Bearbeitungsverfahren gefertigt. Diese können allerdings grundsätzlich auch aus Metallguss (Aluminiumguss, Stahlguss, Grauguss) hergestellt werden. Vorzugsweise wird die Strömungsmaschine als Radialturbine in einer ORC- Anlage verwendet zur Durchführung eines Organic-Rankine-Kreisprozesses. The guide body 3 " or the deflecting elements 31 and 32 in a turbomachine according to the invention are made of a (noble) steel and are produced by means of machining processes, but these can in principle also be produced from cast metal (cast aluminum, cast steel, cast iron) Preferably, the turbomachine is used as a radial turbine in an ORC plant for performing an Organic Rankine cycle.
Im Sinne der vorliegenden Erfindung wird als Strömungsmaschine insbesondere auch eine Turbinensystem bezeichnet, in dem ein dampfförmiges Ar- beitsmedium unter einem Druck einströmt, in einem feststehenden Düsensystem, auch mit Leitbeschaufelung, entspannt und hierbei beschleunigt wird. Nach dem Düsensystem wird der Dampf darin durch ein rotierendes Schaufelsystem umgelenkt, eventuell weiter entspannt und gibt dabei seine Strömungsenergie über die Schaufeln an eine mit den Schaufeln verbundene bzw. gekoppelte Welle ab. Von dieser Welle wird die mechanische Rotationsenergie danach zu der weiteren Nutzung an einen Verbraucher oder eine Einrichtung für das Umwandeln von Energie übertragen. Beispielsweise können durch die Welle Einrichtungen für das Umwandeln von Energie in Form von Generatoren für die Stromerzeugung angetrieben werden. Die Erfindung bewirkt mit einfachen und preiswerten Leitkörpern eine Effizienzerhöhung von Radialturbinen. Mit einer erfindungsgemäßen Strömungsmaschine kann so der Wirkungsgrad einer ORC-Anlage verbessert werden. Zusammenfassend sind insbesondere folgende bevorzugte Merkmale der Erfindung festzuhalten: Eine Strömungsmaschine, insbesondere eine Turbine umfasst ein Gehäuse 1 , 4, 1 1 , welches zumindest einen Einströmungskanal 10 aufweist. Dabei sind an einem Laufrad 2 mehrere Schaufeln angeordnet, die von einem Arbeitsmedium anströmbar sind. Das Arbeitsmedium strömt dabei über den Einströmungskanal 10 in mindestens einen zwischen zwei am Laufrad 2 aufgenommenen Schaufeln 21 gebildeten Schaufelkanal 20 ein. Nach dem Austritt aus dem Laufradbereich tritt das Arbeitsmedium in einen Diffusor 4 ein. Dabei ist wenigstens ein Leitkörper 3, 3', 3" für eine Umlenkung des aus dem Schaufelkanal 20 ausströmenden Arbeitsmediums in Richtung des Diffusors 4 vorgesehen. Der Leitkörper in der Strömungsmaschine ist bevorzugt zumindest abschnittsweise in einem von den Laufradschaufeln in radialer Richtung umgebenen Zwischenbereich 29 des Laufrades positioniert, der zwischen einem Schaufelkanalaustritt 23 und einer Eintrittsöffnung 24 in einem dem Laufrad 2 nachgeschalteten von dem Diffusor 4 gebildeten Austrittskanal 40 liegt. Die Erfindung betrifft auch eine Anlage zur Durchführung eines Organic-Rankine-Kreisprozesses mit einer solchen Strömungsmaschine. For the purposes of the present invention, a turbomachine, in particular, in which a vaporous working medium flows under a pressure, is expanded in a stationary nozzle system, even with a guide blade, and in this process is accelerated. After the nozzle system, the steam is deflected therein by a rotating blade system, possibly further relaxed and gives off its flow energy through the blades to a shaft connected to the blades or coupled. From this shaft, the mechanical rotational energy is then transferred to a consumer or a means for converting energy for further use. For example, devices for converting energy in the form of generators for power generation can be driven by the shaft. The invention causes with simple and inexpensive Leitkörper an increase in efficiency of radial turbines. With a turbomachine according to the invention, the efficiency of an ORC system can thus be improved. In summary, the following preferred features of the invention are to be noted in particular: A turbomachine, in particular a turbine, comprises a housing 1, 4, 11, which has at least one inflow passage 10. In this case, a plurality of blades are arranged on an impeller 2, which can be flowed against by a working medium. The working medium in this case flows via the inflow passage 10 into at least one vane passage 20 formed between two vanes 21 accommodated on the impeller 2. After exiting the impeller area, the working medium enters a diffuser 4. In this case, at least one guide body 3, 3 ' , 3 "is provided for a deflection of the working medium flowing out of the blade channel 20 in the direction of the diffuser 4. The guide body in the turbomachine is preferably at least partially in an intermediate region 29 of the radial direction surrounded by the impeller blades Impeller positioned between a blade channel outlet 23 and an inlet opening 24 in a downstream of the impeller 2 formed by the diffuser 4 outlet channel 40. The invention also relates to a system for performing an Organic Rankine cycle with such a turbomachine.
Bezugszeichenliste: LIST OF REFERENCE NUMBERS
I Düsenring I nozzle ring
1 ,4, 1 1 Turbinengehäuse 1, 4, 1 1 turbine housing
2 Laufrad 2 impeller
3, 3', 3" Leitkörper 3, 3 ' , 3 " guide body
4 Diffusor  4 diffuser
5 Strömungsrichtung  5 flow direction
6 Abstände  6 distances
10 Düsenkanal 10 nozzle channel
10 Einströmungskanal  10 inflow channel
I I Abdeckung der Düsen  I I cover the nozzles
20 Schaufelkanal  20 bucket channel
21 Schaufel  21 scoop
22 Bandage an Schaufel 22 bandage on shovel
23 Schaufelaustritt  23 bucket outlet
24 Eintrittsöffnung  24 entrance opening
25 Kante  25 edge
26 Kante  26 edge
27 Rotationsachse 27 rotation axis
28 Leitkontur  28 lead contour
29 Zwischenbereich innerhalb des Laufrads  29 Intermediate area inside the impeller
30 Kanal zwischen den Leitkörpern  30 channel between the guide bodies
31 ,32 Umlenkelemente 31, 32 deflecting elements
33 Verbindungssteg zwischen den Leitkörpern und der Befestigung 33 connecting web between the guide bodies and the attachment
33 Steg  33 footbridge
34 Befestigungsring der Leitkörper am Diffusoreinlauf  34 Mounting ring of the guide body at the diffuser inlet
40 Kanal im Diffusor 40 channels in the diffuser
40 Austrittskanal 40 outlet channel
40 Diffusorkanaleintritt  40 diffuser channel entry
40 Diffusorkanal 42 Strömung zwischen den Schaufeln des Laufrads 40 diffuser channel 42 flow between the blades of the impeller
42,51 Richtungspfeil  42.51 directional arrow
51 Strom  51 electricity
51 Strömung im Düsenkanal  51 Flow in the nozzle channel
52 Strömung im Schaufelkanal 52 flow in the blade channel
53 Strömung zwischen den Leitkörpern  53 Flow between the guide bodies
53 Pfeilrichtung  53 arrow direction
54 Wirbel  54 swirls
54 Strömungsablösung im Diffusor  54 Flow separation in the diffuser
60 Schaufelhöhe am Schaufelkanalaustritt des Laufrads 60 bucket height at the bucket channel exit of the impeller
61 ,62,63 Axialer Abstand 61, 62,63 Axial distance
61 Axialer Abstand zwischen Laufradscheibe und Umlenkelement 61 Axial distance between impeller disc and deflector
62 Axialer Abstand zwischen beiden Umlenkelementen 62 Axial distance between both deflection elements
63 Axialer Abstand zwischen Leitkörper 2 und dem Schaufelkopf bzw. der Bandage  63 Axial distance between the guide body 2 and the blade head or the bandage
100 Düsenkanal  100 nozzle channel
1 10 Turbinengehäuse  1 10 turbine housing
120 Turbinenrad, Laufrad  120 turbine wheel, impeller
121 Schaufel  121 scoop
151 Richtungspfeil 151 directional arrow
153 Arbeitsmediumaustritt  153 working fluid outlet

Claims

Patentansprüche claims
1 . Strömungsmaschine mit einem Gehäuse (1 ,4, 1 1 ), das zumindest einen Einströmungskanal (10) aufweist, und einem im Gehäuse auf einer Welle drehbar gelagerten Laufrad (2), an dem mehrere Schaufeln (21 ) angeordnet sind, die von einem Arbeitsmedium anströmbar sind, wobei das Arbeitsmedium über den Einströmungskanal (10) in mindestens einen zwischen zwei am Laufrad (2) aufgenommenen Schaufeln (21 ) gebildeten Schaufelkanal (20) einströmt, wobei das Arbeitsmedium nach dessen Austritt aus dem Schaufelkanal (20) in einen Zwischenbereich1 . Turbomachine with a housing (1, 4, 1 1) having at least one inflow passage (10), and a rotatably mounted in the housing on a shaft impeller (2) on which a plurality of blades (21) are arranged, of a working medium can flow against, wherein the working medium via the inflow passage (10) in at least one formed between two impeller (2) blades (21) formed blade channel (20) flows, wherein the working fluid after its exit from the blade channel (20) in an intermediate region
(29) eintritt, der zwischen einem Schaufelkanalaustritt (23) und einer Eintrittsöffnung (24) in einem dem Laufrad (20) nachgeschalteten Austrittskanal (40) liegt, und wobei für eine Umlenkung des aus dem Schaufelkanal (20) ausströmenden Arbeitsmediums in Richtung des Austrittskanals (40) wenigstens ein Leitkörper (3, 3', 3") mit mindestens einem Umlenkelement (31 , 32) in dem Zwischenbereich (29) zwischen dem Schaufelkanalaustritt (23) und dem Austrittskanal (40) vorgesehen ist. (29) enters, which between a Schaufelkanalaustritt (23) and an inlet opening (24) in the impeller (20) downstream outlet channel (40), and wherein for a deflection of the effluent from the blade channel (20) working medium in the direction of the outlet channel (40) at least one guide body (3, 3 ' , 3 " ) is provided with at least one deflecting element (31, 32) in the intermediate region (29) between the Schaufelkanalaustritt (23) and the outlet channel (40).
2. Strömungsmaschine nach Anspruch 1 , dadurch gekennzeichnet, dass der Leitkörper (3') in den Austrittskanal (40) ragt. 2. Turbomachine according to claim 1, characterized in that the guide body (3 ' ) in the outlet channel (40) protrudes.
3. Strömungsmaschine nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass das Arbeitsmedium über einen sich erweiternden Einströ- mungskanal (10) auf das Laufrad (2) in radialer Richtung zu einer Rotationsachse (27) des Laufrades (2) einströmt. 3. Turbomachine according to claim 1 or 2, characterized in that the working medium via a flared inflow channel (10) on the impeller (2) in the radial direction to a rotational axis (27) of the impeller (2) flows.
4. Strömungsmaschine nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass der Leitkörper (3',3") ein Umlenkelement (31 , 32) mit einer ersten und einer zweiten ringförmigen Kante (25, 26) aufweist, wobei die erste Kante (25) des Umlenkelements (31 , 32) benachbart zu dem Schaufelkanalaustritt (23) positioniert ist, und wobei die zweite Kante (26) benachbart zu der Eintrittsöffnung (24) in dem Austrittskanal (40) angeordnet ist. 4. Turbomachine according to one of claims 1 to 3, characterized in that the guide body (3 ' , 3 " ), a deflecting element (31, 32) having a first and a second annular edge (25, 26), wherein the first edge (25) of the deflecting element (31, 32) is positioned adjacent to the blade channel exit (23), and wherein the second Edge (26) adjacent to the inlet opening (24) in the outlet channel (40) is arranged.
Strömungsmaschine nach Anspruch 4, dadurch gekennzeichnet, dass die erste Kante (25) eine Anströmkante und die zweite Kante (26) eine Abströmkante ist. Turbomachine according to claim 4, characterized in that the first edge (25) is a leading edge and the second edge (26) is a trailing edge.
Strömungsmaschine nach Anspruch 4 oder 5, dadurch gekennzeichnet, dass das Umlenkelement (31 , 32) mit einer Leitkontur (28) ausgebildet ist, die sich von der ersten Kante (25) aus einer zu einer Rotationsachse (27) des Laufrades (2) radialen Richtung zu der zweiten Kante (26) in eine zu der Rotationsachse (27) des Laufrades (2) axiale Richtung erstreckt, um aus dem Schaufelkanal (20) ausströmendes Arbeitsmedium aus der radialen in die axiale Richtung umzulenken. Turbomachine according to claim 4 or 5, characterized in that the deflecting element (31, 32) is formed with a guide contour (28) extending from the first edge (25) from one to a rotational axis (27) of the impeller (2) radial Direction to the second edge (26) in an axial direction to the axis of rotation (27) of the impeller (2) extends to redirect from the blade channel (20) effluent working fluid from the radial to the axial direction.
7. Strömungsmaschine nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass das Umlenkelement (31 ,32) eine dem Laufrad (2) zugewandte und eine dem Laufrad (2) abgewandte Seite umfasst und derart positioniert ist, dass es vom Arbeitsmedium beidseitig umström- bar ist. 7. Turbomachine according to one of claims 1 to 6, characterized in that the deflecting element (31, 32) facing the impeller (2) and the impeller (2) side facing away and is positioned so that it flows around the working medium on both sides - is bar.
8. Strömungsmaschine nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass der Leitkörper (3") mehrere voneinander beab- standete Umlenkelemente (31 , 32) aufweist, die zusammen ein durch- strömbares Gitter bilden, in dem der Gesamtstrom des Arbeitsmediums in mehrere ringförmige Teilströme unterteilt wird. 8. Turbomachine according to one of claims 1 to 7, characterized in that the guide body (3 " ) a plurality of spaced-apart deflecting elements (31, 32), which together form a flow-through grid, in which the total flow of the working medium in a plurality of annular partial streams is divided.
9. Strömungsmaschine nach Anspruch 8, dadurch gekennzeichnet, dass wenigstens ein Umlenkelement (31 , 32) eine tropfenförmige, halbmond- förmige oder tragf lügeiförmige Querschnittsgeometrie aufweist. 9. Turbomachine according to claim 8, characterized in that at least one deflecting element (31, 32) has a teardrop-shaped, crescent-shaped or Tragf liege-shaped cross-sectional geometry.
Strömungsmaschine nach Anspruch 8 oder 9, dadurch gekennzeichnet, dass die voneinander beabstandeten Umlenkelemente (31 , 32) derart positioniert sind, dass deren den Schaufeln (21 ) des Laufrades (2) zugewandte Kanten in axialer Richtung einen axialen Abstand (62) aufweisen. Turbomachine according to claim 8 or 9, characterized in that the deflecting elements (31, 32) spaced from each other are positioned such that their blades (21) of the impeller (2) facing edges in the axial direction an axial distance (62).
Strömungsmaschine nach einem der Ansprüche 8 bis 10, dadurch gekennzeichnet, dass die voneinander beabstandeten Umlenkelemente (31 , 32) derart positioniert sind, dass deren in Richtung der Rotationsachse (27) des Laufrads (2) weisenden Kanten (25, 26) einen unterschiedlichen radialen Abstand bezüglich der Rotationsachse (27) des Laufrads (2) aufweisen. Turbomachine according to one of claims 8 to 10, characterized in that the mutually spaced deflection elements (31, 32) are positioned such that their in the direction of the axis of rotation (27) of the impeller (2) facing edges (25, 26) a different radial Distance with respect to the axis of rotation (27) of the impeller (2).
Strömungsmaschine nach Anspruch 1 1 , dadurch gekennzeichnet, dass der radiale Abstand der ersten Kante (25) von der Rotationsachse (27) des Laufrads (2) größer ist als der radiale Abstand der zweiten Kante (26) von der Rotationsachse (27) des Laufrads (2). Turbomachine according to claim 1 1, characterized in that the radial distance of the first edge (25) from the axis of rotation (27) of the impeller (2) is greater than the radial distance of the second edge (26) from the axis of rotation (27) of the impeller (2).
Strömungsmaschine nach einem der Ansprüche 1 bis 12, dadurch gekennzeichnet, dass an einer mit dem Laufrad (2) verbundenen Welle mehrere Permanentmagneten und/oder Rotorwicklungen angeordnet sind, die mit mehreren benachbart angeordneten, die Welle umgreifenden Statorwicklungen einen elektrischen Generator bilden. Turbomachine according to one of claims 1 to 12, characterized in that on a shaft connected to the impeller (2) a plurality of permanent magnets and / or rotor windings are arranged, which with a plurality of adjacently arranged, the shaft encompassing stator windings form an electrical generator.
14. Verwendung einer gemäß einem der Ansprüche 1 bis 12 ausgebildeten Strömungsmaschine als Turbine, insbesondere als Radialturbine, in einem Organic-Rankine-Kreisprozess oder als Verdichter von gasförmigem Medium, indem das gasförmige Medium durch Anströmen des Leitkörpers (3, 3', 3") zu den Schaufeln (21 ) geleitet wird. 14. Use of a trained according to one of claims 1 to 12 turbomachine as a turbine, in particular as a radial turbine, in an Organic Rankine cycle or as a compressor of gaseous medium by the gaseous medium by flow of the guide body (3, 3 ' , 3 " ) is directed to the blades (21).
15. Anlage zur Durchführung eines Organic-Rankine-Kreisprozesseses mit einem Kondensator zur Verflüssigung eines in der Anlage umgewälzten Arbeitsmediums, einer Pumpe, einem Verdampfer zur Verdampfung des Arbeitsmediums sowie einer dem Verdampfer nachgeschalteten Strömungsmaschine, insbesondere einer Turbine, in der das Arbeitsmedium unter Entnahme von Energie aus dem Kreislauf entspannt wird, wobei die Strömungsmaschine nach einem der Ansprüche 1 bis15. Plant for performing an Organic Rankine cycle with a condenser for liquefying a circulated in the plant Working medium, a pump, an evaporator for evaporation of the working medium and a downstream of the evaporator flow machine, in particular a turbine in which the working fluid is expanded while removing energy from the circulation, wherein the turbomachine according to one of claims 1 to
13 ausgeführt ist. 13 is executed.
EP11802969.3A 2010-12-30 2011-12-30 Turbomachine Active EP2659093B1 (en)

Priority Applications (1)

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EP18209322.9A EP3480425B1 (en) 2010-12-30 2011-12-30 Radial turbine

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE202010017157U DE202010017157U1 (en) 2010-12-30 2010-12-30 Efficiency enhancement facilities for radial turbines in ORC plants
DE201010056557 DE102010056557A1 (en) 2010-12-30 2010-12-30 Radial turbine for use in organic rankine cycle system for conversion of flow energy of working medium into torque to drive electrical generator, has conducting body, where steam operatively circulates around sides of conducting body
PCT/EP2011/074330 WO2012089837A1 (en) 2010-12-30 2011-12-30 Turbomachine

Related Child Applications (1)

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EP18209322.9A Division EP3480425B1 (en) 2010-12-30 2011-12-30 Radial turbine

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EP2659093A1 true EP2659093A1 (en) 2013-11-06
EP2659093B1 EP2659093B1 (en) 2018-12-05

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EP18209322.9A Active EP3480425B1 (en) 2010-12-30 2011-12-30 Radial turbine
EP11802969.3A Active EP2659093B1 (en) 2010-12-30 2011-12-30 Turbomachine

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DE102013203448A1 (en) 2013-02-28 2014-08-28 Dürr Systems GmbH Plant and method for treating and / or utilizing gaseous medium
DE102014218344B4 (en) 2014-09-12 2023-08-03 Dürr Systems Ag Process and system for separating contaminants from process exhaust air
US11326550B1 (en) 2021-04-02 2022-05-10 Ice Thermal Harvesting, Llc Systems and methods utilizing gas temperature as a power source
US11592009B2 (en) 2021-04-02 2023-02-28 Ice Thermal Harvesting, Llc Systems and methods for generation of electrical power at a drilling rig

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GB877988A (en) * 1957-09-24 1961-09-20 American Mach & Foundry Centripetal compressors
DE1551190A1 (en) * 1966-06-24 1970-01-15 Rudolf Logaida Speed turbine with synchronization stages
US4066381A (en) * 1976-07-19 1978-01-03 Hydragon Corporation Turbine stator nozzles
SU595519A1 (en) * 1976-11-02 1978-02-28 Ордена Ленина И Ордена Трудового Красного Знамени Невский Машиностроительный Завод Им.В.И.Ленина Method of assembling centrifugal turbine machine
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EP0093990B1 (en) * 1982-05-11 1988-04-27 A.G. Kühnle, Kopp &amp; Kausch Steam turbine
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DE202010017157U1 (en) 2010-12-30 2011-03-17 Eckert, Frank Efficiency enhancement facilities for radial turbines in ORC plants

Also Published As

Publication number Publication date
US20130129496A1 (en) 2013-05-23
EP3480425A1 (en) 2019-05-08
US9322414B2 (en) 2016-04-26
EP3480425B1 (en) 2020-09-09
WO2012089837A1 (en) 2012-07-05
EP2659093B1 (en) 2018-12-05

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