EP3265653B1 - Turbine for organic rankine cycles with axial input and output - Google Patents
Turbine for organic rankine cycles with axial input and output Download PDFInfo
- Publication number
- EP3265653B1 EP3265653B1 EP16713990.6A EP16713990A EP3265653B1 EP 3265653 B1 EP3265653 B1 EP 3265653B1 EP 16713990 A EP16713990 A EP 16713990A EP 3265653 B1 EP3265653 B1 EP 3265653B1
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- turbine
- duct
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- outlet
- outlet duct
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- 239000012530 fluid Substances 0.000 claims description 27
- 238000011144 upstream manufacturing Methods 0.000 claims description 11
- 238000007789 sealing Methods 0.000 claims 1
- 238000007493 shaping process Methods 0.000 description 3
- 238000003466 welding Methods 0.000 description 3
- 239000012808 vapor phase Substances 0.000 description 2
- 239000003638 chemical reducing agent Substances 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000009792 diffusion process Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000005192 partition Methods 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
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Classifications
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- 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
- F01D1/04—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 axially
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- 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
- F05D2210/00—Working fluids
- F05D2210/40—Flow geometry or direction
- F05D2210/43—Radial inlet and axial outlet
-
- 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
- F05D2220/00—Application
- F05D2220/30—Application in turbines
- F05D2220/31—Application in turbines in steam turbines
Definitions
- the present invention relates to the field of turbines for gas and steam expansion, in particular for expansion of a working fluid in an organic Rankine cycle (ORC), and specifically relates to improvements to the overall structure of a radial or axial or mixed type turbine, having one or more stages.
- ORC organic Rankine cycle
- the expansion gas and steam turbines essentially comprise a fixed body or housing having an inlet passage and an outlet passage for a working fluid, at least a first stator and any subsequent stators respectively of a first and any subsequent stages of the turbine, a shaft of the turbine rotating around an axis and carrying at least a first rotor and any subsequent rotors associated respectively to the first stator and to any subsequent stators.
- the expression tangential direction in a point of a meridian plane identifies the direction, orthogonal to the meridian plane and orthogonal to a radial direction passing through the point.
- a direction parallel to the rotation axis of the machine is defined axial direction.
- an axial stage of a turbine includes a row of stator blades and a corresponding array of rotor blades, respectively upstream and downstream relative to the direction of mass flow; in turn the flow predominantly occurs due to the axial component of the velocity within the flow.
- a radial turbine stage includes an array of stator blades and a corresponding array of rotor blades, respectively upstream and downstream, with respect to the direction of mass flow; in turn the flow predominantly occurs due to the radial component of the velocity within the flow.
- Document FR2279926 discloses a turbomachine, in particular a steam turbine with a high steam inlet temperature, comprising an annular chamber intended to produce radially extending movement and extending radially outwardly upstream of the first turbine of blades over the entire periphery.
- the first ring of rotating blades being fed axially and directly to the upstream guide vanes, and the turbomachine also comprising individually controllable flow fluid inlets and abutting tangentially in said annular chamber, characterized in that the ring of rotating blade immediately downstream of the annular chamber is disposed on a shaft collar whose diameter is greater than that of the downstream blades.
- Document US3869220 describes a rotary machine comprising at least one row of rotor blades circumferentially distributed on a rotor and disposed in a rotor blade passage between at least one row of upstream stator blades and at least one row of downstream rotor blades is provided with partitions in the upstream and downstream stator blades to provide a plurality of arcuate segmented flowpaths through the rotor blading.
- Figures 1 and 2 show a configuration example of a known type, in which are visible an inlet conduit 1 and an outlet duct 2 of a turbine 100 for ORC systems, the turbine being able to be radial, axial or mixed type. It is also visible an electric generator 3 mechanically connected to the turbine 100 directly or by interposition of a speed reducer.
- the radial outlet ducts 2 can also be of non-circular shape, for example rectangular.
- One of the characteristics of the use of an organic fluid as the working fluid for a Rankine cycle is that a high volumetric flow rates for entering and exiting the turbine it often required, so as to require large ducts especially in the turbine outlet.
- Subject of the present invention is therefore a turbine having at least one inlet duct for the working fluid feeding whose end portion is oriented along the axial direction and at least one outlet duct for the working fluid delivery, whose initial portion is oriented along the axial direction, as specified in the attached independent claim.
- the following description relates to a turbine 100 in which the mass transport from inlet to outlet of the fluid dynamic path where the expansion occurs is mainly due to the axial component of the fluid speed, and is referred to as axial turbine, or predominantly due to the radial component of the speed and is referred to as a radial turbine, or still as a mixed type turbine. All these types of turbines can be configured so as to have an end portion 10 "of the inlet duct 10 and an initial portion 20' of the outlet duct 20 in which the flow of the working fluid is oriented along the axial direction ( Figures 3 -12 ).
- FIG. 3 shows a generic turbine 100 having inlet ducts 10 in which a portion 10' is radially disposed and said portions converge in a central plenum 14.
- the outlet duct 20 and in particular its initial portion 20' is axially arranged, from the same side of the central plenum 14 with respect to the turbine 100 and has a substantially annular section, defined by an outer side wall 201 and an inner side wall 202.
- the high pressure central plenum 14 must be separated from the annular duct 20.
- This central plenum 14 of the turbine inlet can be separated by means of a flanged cover 9.
- the cover 9 (as shown in Figure 4 ) can have an elongated portion with function of flow distributor, possibly bladed, to confer the desired value of the tangential component to the stator inlet.
- the walls 201 and 202 can be designed to become the diffuser upstream of the exit from the turbine.
- the turbine 100 of Figure 4 is of the axial type, i.e. it comprises a housing 21, at least one stator group 22 comprising an array of stator blades 23, at least a rotor group 24, comprising a corresponding array of rotor blades 25, upstream and downstream, respectively, with respect to the direction of the working fluid, and a turbine shaft 26 that supports the rotor group.
- the flow is mainly due to the axial component of the velocity within the flow.
- the inversion 180° of the flow is achieved by means of shaping 13 internal to the housing 21 of the turbine 100.
- the turbine 100 of Figure 5 is of the radial centrifugal type and also comprises a housing 21, at least one stator group 22 comprising an array of stator blades 23, at least a rotor group 24, comprising a corresponding array of rotor blades 25, upstream and downstream, respectively, with respect to the direction of working fluid, and a turbine shaft 26 that supports the rotor group.
- the flow is mainly due to the radial component of the speed within the flow.
- the inversion 180° of the flow is achieved by means of a deflector cone 15 upstream of the stator group 22 and shaping 13 downstream of the internal rotor 24 inside the housing of the turbine 100.
- the turbine 100 is shown in an alternative configuration still having an inlet duct 10 and an outlet duct 20, in the axial direction.
- the inlet duct 10 comprises a first portion 10' with a radial direction and a second end portion 10 " having an axial direction and in fluid connection with an inlet opening 101 of the turbine 100.
- the steam enters the turbine from the inlet duct 10 and exits through an annular outlet duct 20, in fluid connection with an outlet opening 102 of the turbine 100, which allows a wide outlet section.
- the annular conduit will preferably be configured so as to obtain a gradual reduction of the speed and then carry out a diffusion effect.
- the inlet duct 10 has a rigid structure due to a plurality of fixed constraints, for example weldings 5, present on the two side walls 201,202 of the annular duct 20.
- Figures 7 and 8 show two configurations having a lower structural rigidity.
- the inlet duct 10 is not constrained in a fixed manner to the annular duct 20 but is only fixed with its end portion 10 " to the inlet opening 101 of the turbine 100.
- the configuration of Figure 7 has a central chamber 8, bounded by the inner wall 202 of the outlet duct 20, at atmospheric pressure and in contact with the external environment.
- the chamber 8 is connected to the external environment by means of the hole 16 resulting from the presence of a radial duct 203 welded to the walls 201 and 202 of the outlet duct, and is sealed from the annular duct 20 by means of a seal 12, for example, a seal between the inner wall 202 of the annular duct 20 and the flanged cover 9 ( figure 7 ).
- a seal 12 for example, a seal between the inner wall 202 of the annular duct 20 and the flanged cover 9 ( figure 7 ).
- the configuration shown in Figure 8 show the duct 10 having an outer bellows 11 portion, to allow for thermal expansion, and a central chamber 8.
- Said central chamber 8 is in communication with the outlet opening 102 of the turbine and then has a pressure equal to the outlet of the turbine.
- the element 9 is not present not being necessary to isolate the central chamber 8 from the outlet opening 102.
- FIGS. 9 to 12 are shown configurations in which a flanged cover 9 is not required, because the central chamber 8 may be at the same pressure of the fluid leaving the turbine 100: in fact there is a clearance between the portion 10' of the inlet duct 10 and the hole 16 drilled in the duct 20 at the level of the inner wall 202. In this way, if there were a loss at the connection between the inlet duct 10 in its end portion 10" and the inlet of the turbine 100, the loss would remain within the closed loop of the turbogenerator and should not be dispersed outside.
- the connection between the duct 10 and the outer wall of the annular duct 20 is of fixed type, made for example by means of welding.
- a further configuration presents the inlet duct 10 with a "T"shape, in which the radial portion 10' is the inlet flow and the axial portion 10" is the outlet flow.
- the presence of the bellows 11 and of tie rods 204 makes the "T" joint balanced according to the prior art, that is, a balanced thrusts compensator.
- the connection flange 205 to the turbine 100 has a certain freedom of movement with respect to the inlet duct 10' to which is bound and does not transmit the forces due to the pressure caused by the presence of two bellows 11 according to the prior art.
- a final configuration shown in Fig.12 has the inlet duct 10 realized by means of two radial portions 10' (a double inlet is often required in the presence of larger volume flows at the turbine inlet) and a "T" element, that connects the two radial portions.
- the element 10 is the terminal portion of the duct 10 and is axially arranged. Even this element "T” is balanced with respect to the thrust of the internal pressure due to the presence of bellows 11, according to known techniques.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Turbine Rotor Nozzle Sealing (AREA)
Description
- The present invention relates to the field of turbines for gas and steam expansion, in particular for expansion of a working fluid in an organic Rankine cycle (ORC), and specifically relates to improvements to the overall structure of a radial or axial or mixed type turbine, having one or more stages.
- As is well known and in brief, the expansion gas and steam turbines essentially comprise a fixed body or housing having an inlet passage and an outlet passage for a working fluid, at least a first stator and any subsequent stators respectively of a first and any subsequent stages of the turbine, a shaft of the turbine rotating around an axis and carrying at least a first rotor and any subsequent rotors associated respectively to the first stator and to any subsequent stators. To take good advantages in using heat sources at a not very high temperature or sources with medium-low flow rates, it is necessary to use working fluids, other than water, said working fluid having specific properties, that well fit such sources.
- In the context of the present invention, reference is made, as is frequently customary in the field of turbines, to an axisymmetric coordinate system in which a generic plane on which the axis of rotation of the turbine lies is called the meridian plane. The direction perpendicular to the axis of the machine and lying in the meridian plane is defined radial direction.
- The expression tangential direction in a point of a meridian plane identifies the direction, orthogonal to the meridian plane and orthogonal to a radial direction passing through the point. A direction parallel to the rotation axis of the machine is defined axial direction.
- More in detail, an axial stage of a turbine includes a row of stator blades and a corresponding array of rotor blades, respectively upstream and downstream relative to the direction of mass flow; in turn the flow predominantly occurs due to the axial component of the velocity within the flow. A radial turbine stage includes an array of stator blades and a corresponding array of rotor blades, respectively upstream and downstream, with respect to the direction of mass flow; in turn the flow predominantly occurs due to the radial component of the velocity within the flow.
- Document
FR2279926 - Document USRE29128E discloses a converging-diverging nozzle unit for supersonic expansion in turbines wherein a plurality of converging nozzle segments open into a common di-verging chamber at or near the throat of the converging nozzles. Convergence and divergence may occur in different directions in the nozzle unit.
- Document
US3869220 describes a rotary machine comprising at least one row of rotor blades circumferentially distributed on a rotor and disposed in a rotor blade passage between at least one row of upstream stator blades and at least one row of downstream rotor blades is provided with partitions in the upstream and downstream stator blades to provide a plurality of arcuate segmented flowpaths through the rotor blading. -
Figures 1 and 2 show a configuration example of a known type, in which are visible aninlet conduit 1 and anoutlet duct 2 of aturbine 100 for ORC systems, the turbine being able to be radial, axial or mixed type. It is also visible anelectric generator 3 mechanically connected to theturbine 100 directly or by interposition of a speed reducer. The organic fluid in vapor phase coming from theinlet duct 1 oriented axially, through the interior of the turbine and exits from theoutlet duct 2 according to a radial direction. In some configurations theradial outlet ducts 2 can also be of non-circular shape, for example rectangular. - One of the characteristics of the use of an organic fluid as the working fluid for a Rankine cycle is that a high volumetric flow rates for entering and exiting the turbine it often required, so as to require large ducts especially in the turbine outlet.
- One of the drawbacks of the turbines for ORC systems, as described above, is represented by the fact that, due to geometrical constraints linked to the overall dimension of the machine and the housing, in known solutions, the turbines having one or more radial outlet ducts, are characterized by an area of said ducts not sufficiently large to allow a high volume flow with low speed and therefore low losses at the inlet of these ducts and / or in the ducts themselves. To limit the speed, this area should be significantly higher than the discharge surface between the vanes of the last stage, that is equal to an annular element if the outlet of the turbine is axial or to a lateral area of a cylinder if the outlet of the turbine is radial. To a lesser extent, due to the reduced volumetric flow rate, the same problem is also proposed for the inlet ducts of the radial type (if the inlet pressure is relatively low may be necessary to adopt more radial inlets on the same turbine). Therefore, turbines having radial inlets and radial outlets have the disadvantage of not allowing very high volumetric flows, as often required by ORC systems, having low losses. Furthermore, such turbines bind the connection layout of the turbine itself to the rest of the system.
- Therefore, there is a need to obtain an innovative turbine for Organic Rankine cycle system able to overcome the drawbacks of the known turbines.
- Subject of the present invention is therefore a turbine having at least one inlet duct for the working fluid feeding whose end portion is oriented along the axial direction and at least one outlet duct for the working fluid delivery, whose initial portion is oriented along the axial direction, as specified in the attached independent claim.
- The dependent claims describe further details and advantageous aspects of the invention.
- The different modes of the invention will now be described, by way of examples, with reference to the attached drawings in which:
-
Figure 1 shows a side view of a turbine having an inlet with an axial duct and an outlet with a radial duct, according to the prior art; -
Figure 2 shows a front view of the turbine ofFig.1 ; -
Figure 3 shows a partial cross section of a turbine having two radial inlets, with an axial plenum and an outlet with axial duct, according to the present invention; -
Figure 4 shows a cross section of an axial turbine with inlet and outlet ducts configuration as inFigure 3 and also illustrates the path of the fluid inside the machine, which comprises at least one axial stage; -
Figure 5 shows a cross section of a radial turbine with inlet and outlet ducts configuration as inFigure 3 and also illustrates the path of the fluid inside the machine, which comprises at least one radial outflow stage; -
Figure 6 shows a partial cross section of a turbine having an axial inlet and an axial outlet, according to a first design solution; -
Figure 7 shows a partial cross section of a turbine having a second design solution of the inlet and outlet ducts with respect to the turbine ofFigure 6 ; -
Figure 8 shows a partial cross section of a turbine having a third design solution of the inlet and outlet ducts with respect to the turbine ofFigure 6 ; -
Figure 9 shows a partial cross section of a turbine having a fourth design solution of the input and outlet ducts with respect to the turbine ofFigure 6 ; -
Figure 10 shows a partial cross section of a turbine having a fifth design solution of the input and outlet ducts with respect to the turbine ofFigure 6 ; -
Figure 11 shows a partial cross section of a turbine having a sixth design solution of the input and outlet ducts with respect to the turbine ofFigure 6 ; -
Figure 12 shows a partial cross section of a turbine with radial double inlet having a seventh design solution of the inlet and outlet ducts with respect to the turbine ofFigure 6 . - The following description relates to a
turbine 100 in which the mass transport from inlet to outlet of the fluid dynamic path where the expansion occurs is mainly due to the axial component of the fluid speed, and is referred to as axial turbine, or predominantly due to the radial component of the speed and is referred to as a radial turbine, or still as a mixed type turbine. All these types of turbines can be configured so as to have anend portion 10 "of theinlet duct 10 and an initial portion 20' of theoutlet duct 20 in which the flow of the working fluid is oriented along the axial direction (Figures 3 -12 ). - The configuration of
Figure 3 shows ageneric turbine 100 having inletducts 10 in which a portion 10' is radially disposed and said portions converge in acentral plenum 14. Thus, the organic fluid in vapor phase coming from saidinlet ducts 10 does not directly enter into theturbine 100, but accesses to thecentral plenum 14 and subsequently passes through theturbine 100 and through its stator and rotor stages. Theoutlet duct 20 and in particular its initial portion 20' is axially arranged, from the same side of thecentral plenum 14 with respect to theturbine 100 and has a substantially annular section, defined by anouter side wall 201 and aninner side wall 202. The high pressurecentral plenum 14 must be separated from theannular duct 20. Thiscentral plenum 14 of the turbine inlet can be separated by means of a flangedcover 9. The cover 9 (as shown inFigure 4 ) can have an elongated portion with function of flow distributor, possibly bladed, to confer the desired value of the tangential component to the stator inlet. - Also, the
walls - The fact that this embodiment of the invention, and all others that will be described below is applicable to a generic turbine (axial, radial or mixed type) is schematically illustrated in
Figures 4 and5 . In fact, in said figures two types ofturbine 100 are shown. In particular, theturbine 100 ofFigure 4 is of the axial type, i.e. it comprises ahousing 21, at least onestator group 22 comprising an array ofstator blades 23, at least arotor group 24, comprising a corresponding array ofrotor blades 25, upstream and downstream, respectively, with respect to the direction of the working fluid, and aturbine shaft 26 that supports the rotor group. In this turbine the flow is mainly due to the axial component of the velocity within the flow. The inversion 180° of the flow is achieved by means of shaping 13 internal to thehousing 21 of theturbine 100. Theturbine 100 ofFigure 5 is of the radial centrifugal type and also comprises ahousing 21, at least onestator group 22 comprising an array ofstator blades 23, at least arotor group 24, comprising a corresponding array ofrotor blades 25, upstream and downstream, respectively, with respect to the direction of working fluid, and aturbine shaft 26 that supports the rotor group. In this turbine the flow is mainly due to the radial component of the speed within the flow. The inversion 180° of the flow is achieved by means of adeflector cone 15 upstream of thestator group 22 and shaping 13 downstream of theinternal rotor 24 inside the housing of theturbine 100. - With reference to
Figure 6 , theturbine 100 is shown in an alternative configuration still having aninlet duct 10 and anoutlet duct 20, in the axial direction. In particular, theinlet duct 10 comprises a first portion 10' with a radial direction and asecond end portion 10 " having an axial direction and in fluid connection with an inlet opening 101 of theturbine 100. The steam enters the turbine from theinlet duct 10 and exits through anannular outlet duct 20, in fluid connection with an outlet opening 102 of theturbine 100, which allows a wide outlet section. The annular conduit will preferably be configured so as to obtain a gradual reduction of the speed and then carry out a diffusion effect. Theinlet duct 10 has a rigid structure due to a plurality of fixed constraints, forexample weldings 5, present on the two side walls 201,202 of theannular duct 20. - In the following we will describe some variants of the previous solution.
- The configurations shown in Figures from 7 to 12, show how the
inlet duct 10 to be designed so as to be inserted in thehole 16 drilled in theannular duct 20. However, if this is not possible in some alternative configuration, theinlet duct 10 can be divided into more pieces that will then be welded under construction. -
Figures 7 and 8 show two configurations having a lower structural rigidity. Infact, theinlet duct 10 is not constrained in a fixed manner to theannular duct 20 but is only fixed with itsend portion 10 " to the inlet opening 101 of theturbine 100. In particular, the configuration ofFigure 7 has acentral chamber 8, bounded by theinner wall 202 of theoutlet duct 20, at atmospheric pressure and in contact with the external environment. In fact, thechamber 8 is connected to the external environment by means of thehole 16 resulting from the presence of aradial duct 203 welded to thewalls annular duct 20 by means of aseal 12, for example, a seal between theinner wall 202 of theannular duct 20 and the flanged cover 9 (figure 7 ). The configuration shown inFigure 8 , show theduct 10 having an outer bellows 11 portion, to allow for thermal expansion, and acentral chamber 8. Saidcentral chamber 8 is in communication with the outlet opening 102 of the turbine and then has a pressure equal to the outlet of the turbine. Theelement 9 is not present not being necessary to isolate thecentral chamber 8 from theoutlet opening 102. - Also in Figures from 9 to 12 are shown configurations in which a
flanged cover 9 is not required, because thecentral chamber 8 may be at the same pressure of the fluid leaving the turbine 100: in fact there is a clearance between the portion 10' of theinlet duct 10 and thehole 16 drilled in theduct 20 at the level of theinner wall 202. In this way, if there were a loss at the connection between theinlet duct 10 in itsend portion 10" and the inlet of theturbine 100, the loss would remain within the closed loop of the turbogenerator and should not be dispersed outside. The connection between theduct 10 and the outer wall of theannular duct 20 is of fixed type, made for example by means of welding. - A further configuration, as shown in
Figs. 10 and11 , presents theinlet duct 10 with a "T"shape, in which the radial portion 10' is the inlet flow and theaxial portion 10" is the outlet flow. The presence of thebellows 11 and oftie rods 204 makes the "T" joint balanced according to the prior art, that is, a balanced thrusts compensator. In fact, theconnection flange 205 to theturbine 100 has a certain freedom of movement with respect to the inlet duct 10' to which is bound and does not transmit the forces due to the pressure caused by the presence of twobellows 11 according to the prior art. - In
Figure 11 , a different solution for this "T" element is represented: this solution while maintaining the balance of the thrusts can be diverted to a more gradual transition of the flow from the radial direction 10' to theaxial direction 10". - A final configuration shown in
Fig.12 , has theinlet duct 10 realized by means of two radial portions 10' (a double inlet is often required in the presence of larger volume flows at the turbine inlet) and a "T" element, that connects the two radial portions. Theelement 10 "is the terminal portion of theduct 10 and is axially arranged. Even this element "T" is balanced with respect to the thrust of the internal pressure due to the presence ofbellows 11, according to known techniques. - Although at least one exemplary embodiment has been presented in the summary and in the detailed description, it should be understood that there is a large number of variants falling within scope of the invention. It must also be understood that the realization or the presented works are only examples that are not intended to limit in any way the scope of protection of the invention or its application or its configuration. Rather, the summary and the detailed description of the technical expert to provide a convenient guide sector to implement at least one exemplary embodiment, being well clear that numerous variations can be made in the function and assembly of the elements described herein, without departing from the scope of the invention as determined by the appended claims and their technical-legal equivalents.
-
- 100 turbine
- 1, 10 inlet duct
- 2, 20 outlet duct
- 3 generator
- 5 welding
- 10', 10 "respectively radial and axial part of the
inlet duct 10 - 8 central chamber with possible speaker function
- 9 flange cover
- 11 bellows
- 12 seal
- 13 shaping
- 14 central turbine inlet plenum
- 15 cone deflector
- 16 hole in the outlet duct
- 20' initial portion of the
outlet duct 20 - 21 housing
- 22 stator group
- 23 stator blades
- 24 rotor group
- 25 rotor blades
- 26 turbine shaft
- 101 inlet opening of the turbine
- 102 outlet opening of the turbine
- 201,202 side walls of the annular duct
- 203 radial duct welded to the
walls - 204 tie rods
- 205 flange
Claims (9)
- Expansion turbine (100) for a working fluid in an organic Rankine cycle, comprising a housing (21), at least one inlet duct (10) for working fluid feeding and an outlet duct (20) for working fluid discharge, at least one statoric group (22) comprising a statoric blades array (23), at least a rotoric group (24), comprising corresponding rotoric blades array (25), respectively upstream and downstream of the working fluid direction, and a turbine shaft (26) which supports the rotoric group and being said turbine (100), wherein at least one end portion (10 ", 14) of the inlet duct (10), in fluid connection with an inlet opening (101) of the turbine (100), is oriented in an axial direction and at least an initial portion (20') of the outlet duct (20) in fluid connection with an outlet opening (102) of the turbine (100), is oriented in the axial direction and that said end portions (10", 14) of the inlet duct (10) and said initial portion (20') of the outlet duct (20) are both arranged on one end of the housing (21), said expansion turbine (100) being characterized in that:- at least one inlet duct (10) has a portion (10') radially arranged and an end portion shaped as a central plenum (14) and said at least an outlet duct (20) is axially arranged at least in its initial portion (20 '), on the same side of the central plenum (14),- said central plenum (14) of the turbine inlet is separated by the outlet duct (20) by means of a flanged cover (9).
- Turbine (100) according to claim 1, wherein said outlet duct (20) has a substantially annular section, delimited by an outer side wall (201) and an inner side wall (202).
- Turbine (100) according to claim 1 or 2, wherein said at least one inlet duct (10) has a portion (10') radially disposed and a second end portion (10"), connected to the first portion and having an axial direction.
- Turbine (100) according to claim 3, wherein said inlet duct (10) is steadily connected to the two side walls (201, 202) of the outlet duct (20).
- Turbine (100) according to claim 3, wherein said inlet duct (10) is steadily connected to its end portion (10") to the inlet opening (101) of the turbine (100) and has a radial portion (10 ') passing through a hole (16) of the outlet duct (20), and isolated from said outlet duct (20), by means of an annular duct (203).
- Turbine (100) according to claim 3, further comprising a central chamber (8), delimited by an inner wall (202) of the outlet duct (20), connected to the outside through a hole (16), and sealed by the annular duct (20) by means of a seal (12) between the inner wall (202) of the annular duct (20) and the flanged cover (9).
- Turbine (100) according to claim 5, wherein said inlet duct (10) has an external bellows (11), for sealing towards outside outside and for allowing thermal expansions.
- Turbine (100) according to claim 1 or 2, wherein said at least one inlet duct (10) is realized as a balanced thrust compensator, "T" shaped, by means of bellows (11) and tie rods (204).
- Turbine (100) according to claim 1 or 2, wherein said inlet duct (10) has two radial portions (10') and a balanced thrust compensator "T" shaped.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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ITBS20150032 | 2015-03-05 | ||
PCT/IB2016/051121 WO2016139574A1 (en) | 2015-03-05 | 2016-03-01 | Turbine for organic rankine cycles with axial input and output |
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EP3265653A1 EP3265653A1 (en) | 2018-01-10 |
EP3265653B1 true EP3265653B1 (en) | 2019-05-15 |
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CN109098857B (en) * | 2018-08-24 | 2019-08-20 | 西安航天动力研究所 | A kind of rocket engine turbine inlet pipe structure |
CN114183210A (en) * | 2021-12-02 | 2022-03-15 | 中国船舶重工集团公司第七0三研究所 | Compact cylinder structure |
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GB1420600A (en) * | 1972-02-23 | 1976-01-07 | Secr Defence | Rotary bladed compressors |
USRE29128E (en) * | 1973-05-21 | 1977-02-01 | Vaneless supersonic nozzle | |
DE2435153B2 (en) * | 1974-07-22 | 1977-06-30 | Kraftwerk Union AG, 4330 Mülheim | TURBO MACHINE, IN PARTICULAR STEAM TURBINE WITH HIGH STEAM INLET TEMPERATURE |
EA014075B1 (en) * | 2006-04-14 | 2010-08-30 | Геннадий Михайлович МОРГУНОВ | The bladed machine (versions) |
US8221073B2 (en) * | 2008-12-22 | 2012-07-17 | Pratt & Whitney Canada Corp. | Exhaust gas discharge system and plenum |
JP5606473B2 (en) * | 2012-02-24 | 2014-10-15 | 株式会社東芝 | Steam turbine |
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2016
- 2016-03-01 WO PCT/IB2016/051121 patent/WO2016139574A1/en active Application Filing
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WO2016139574A1 (en) | 2016-09-09 |
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