EP3265653A1 - Turbine for organic rankine cycles with axial input and output - Google Patents

Turbine for organic rankine cycles with axial input and output

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Publication number
EP3265653A1
EP3265653A1 EP16713990.6A EP16713990A EP3265653A1 EP 3265653 A1 EP3265653 A1 EP 3265653A1 EP 16713990 A EP16713990 A EP 16713990A EP 3265653 A1 EP3265653 A1 EP 3265653A1
Authority
EP
European Patent Office
Prior art keywords
turbine
duct
inlet
outlet
outlet duct
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
EP16713990.6A
Other languages
German (de)
French (fr)
Other versions
EP3265653B1 (en
Inventor
Roberto Bini
Mario Gaia
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.)
Turboden SpA
Original Assignee
Turboden SpA
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Filing date
Publication date
Application filed by Turboden SpA filed Critical Turboden SpA
Publication of EP3265653A1 publication Critical patent/EP3265653A1/en
Application granted granted Critical
Publication of EP3265653B1 publication Critical patent/EP3265653B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • 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
    • 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.
  • 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.
  • FIG. 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
  • FIG. 2 shows a front view of the turbine of Fig.l
  • FIG. 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 in Figure 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 in Figure 3 and also illustrates the path of the fluid inside the machine, which comprises at least one radial outflow stage;
  • FIG. 6 shows a partial cross section of a turbine having an axial inlet and an axial outlet, according to a first design solution
  • FIG. 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 of Figure 6;
  • FIG. 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 of Figure 6;
  • FIG. 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 of Figure 6;
  • FIG. 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 of Figure 6;
  • FIG. 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 of Figure 6;
  • FIG. 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 of Figure 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 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)

Abstract

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), characterized in that 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).

Description

TURBINE FOR ORGANIC RANKINE CYCLES WITH AXIAL INPUT AND OUTPUT 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.
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 organic fluid in vapor phase coming from the inlet duct 1 oriented axially, through the interior of the turbine and exits from the outlet duct 2 according to a radial direction. In some configurations 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.
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 of Fig.l;
- 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 in Figure 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 in Figure 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 of Figure 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 of Figure 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 of Figure 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 of Figure 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 of Figure 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 of Figure 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 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).
The configuration of Figure 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. Thus, the organic fluid in vapor phase coming from said inlet ducts 10 does not directly enter into the turbine 100, but accesses to the central plenum 14 and subsequently passes through the turbine 100 and through its stator and rotor stages. 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. Also, the walls 201 and 202 can be designed to become the diffuser upstream of the exit from the turbine.
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 and 5. In fact, in said figures two types of turbine 100 are shown. In particular, 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. 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 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. 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 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.
With reference to Figure 6, the turbine 100 is shown in an alternative configuration still having an inlet duct 10 and an outlet duct 20, in the axial direction. In particular, 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.
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 the hole 16 drilled in the annular duct 20. However, if this is not possible in some alternative configuration, the inlet 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, 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. In particular, 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. In fact, 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). 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.
Also in Figures from 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, as shown in Figs. 10 and 11, 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. In fact, 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.
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 the axial direction 10".
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.
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.
REFERENCE NUMBER
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 201, 202 204 tie rods
205 flange

Claims

1. 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).
2. 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).
3. 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.
4. 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).
5. 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).
6. 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).
7. 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.
8. 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 ).
9. 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.
EP16713990.6A 2015-03-05 2016-03-01 Turbine for organic rankine cycles with axial input and output Active EP3265653B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
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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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
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US8221073B2 (en) * 2008-12-22 2012-07-17 Pratt & Whitney Canada Corp. Exhaust gas discharge system and plenum
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