US20150082793A1 - Device for power generation according to a rankine cycle - Google Patents

Device for power generation according to a rankine cycle Download PDF

Info

Publication number
US20150082793A1
US20150082793A1 US14/390,284 US201314390284A US2015082793A1 US 20150082793 A1 US20150082793 A1 US 20150082793A1 US 201314390284 A US201314390284 A US 201314390284A US 2015082793 A1 US2015082793 A1 US 2015082793A1
Authority
US
United States
Prior art keywords
vapour
turbine
evaporator
ring
inlet port
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US14/390,284
Other languages
English (en)
Inventor
Luc Maîtrejean
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.)
Equitherm Sa Rl
Original Assignee
Equitherm Sa Rl
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Equitherm Sa Rl filed Critical Equitherm Sa Rl
Publication of US20150082793A1 publication Critical patent/US20150082793A1/en
Assigned to EQUITHERM S.À R.L. reassignment EQUITHERM S.À R.L. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: MAÎTREJEAN, Luc
Abandoned legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
    • F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
    • F01K25/10—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours the vapours being cold, e.g. ammonia, carbon dioxide, ether
    • 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
    • F01D1/023—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 the working-fluid being divided into several separate flows ; several separate fluid flows being united in a single flow; the machine or engine having provision for two or more different possible fluid flow paths
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/02—Blade-carrying members, e.g. rotors
    • F01D5/04—Blade-carrying members, e.g. rotors for radial-flow machines or engines
    • F01D5/043—Blade-carrying members, e.g. rotors for radial-flow machines or engines of the axial inlet- radial outlet, or vice versa, type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K11/00—Plants characterised by the engines being structurally combined with boilers or condensers
    • F01K11/02—Plants characterised by the engines being structurally combined with boilers or condensers the engines being turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K13/00—General layout or general methods of operation of complete plants
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K3/00—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein
    • F01K3/02—Use of accumulators and specific engine types; Control thereof
    • F01K3/04—Use of accumulators and specific engine types; Control thereof the engine being of multiple-inlet-pressure type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2210/00—Working fluids
    • F05D2210/40—Flow geometry or direction
    • F05D2210/42—Axial inlet and radial outlet

Definitions

  • the present invention generally relates to a device for power generation according to a Rankine Cycle, in particular to an Organic Rankine Cycle (ORC).
  • ORC Organic Rankine Cycle
  • low temperature sources include e.g. industrial waste heat, low temperature geothermal heat sources, low temperature biomass energy and low temperature solar energy, but also novel low temperature heat generators based on chemical or nuclear reactions.
  • ORC Organic Rankine Cycle
  • the working principle underlying the ORC is basically the same as that of the classical Rankine cycle in which the working fluid is water.
  • the ORC uses as working fluid an organic fluid with lower evaporation temperatures than water. It follows that for the same pressure, the evaporation of the organic fluid takes place at a lower temperature than the evaporation of water in a classical Rankine cycle.
  • the external heat source in an ORC may be in a lower temperature range than the external heat source in a Rankine cycle working with water.
  • a basic ORC comprises following main steps.
  • a condensate pump pressurizes in a liquid phase the condensed organic working fluid collected at a condenser.
  • the pressurized organic working fluid is heated and evaporated in an evaporator, by heat exchange with an external heat source.
  • the evaporation temperature in an ORC is generally lower than 200° C., most often in the range of 100° C. to 160° C., and that the vapour is generally no super-heated.
  • the vapour produced in the evaporator flows through an expansion machine, wherein its expansion generates a torque for driving an electrical generator.
  • the vapour is condensed in the condenser, which is cooled by heat exchange with an external cold source.
  • the condensate collected at the condenser is again pressurized in the condensate pump and pumped back into the evaporator.
  • regenerator i.e. a counter-current heat exchanger, which is arranged between the turbine outlet and the condenser inlet.
  • the organic fluid is a “dry fluid”, i.e. if it has a positive or isentropic saturation vapour curve, the vapour of the organic fluid has not reached the two-phase state when it leaves the turbine. It follows that the temperature of the expanded vapour is still considerably higher than the condensing temperature in the condenser. In the regenerator, this temperature difference is used to preheat the pressurized condensate before it enters into the evaporator.
  • the external heat source is connected into the ORC with a heat carrier medium, which has to be cooled down in an evaporator working as counter-current heat exchanger, it is also known to operate an ORC with more than one evaporator.
  • Each evaporator then works at a different evaporation pressure, i.e. with a different evaporation temperature, in combination either with a separate expansion machine for each evaporator or with a single multi-stage expansion machine, in which the vapour produced in each additional evaporator, is injected into an intermediate stage of the multi-stage expansion machine.
  • ORC systems with more than one evaporator are e.g. described in DE 10 2007 044 625 A1.
  • the system comprises several separate ORCs, each of these ORCs comprising an evaporator, a turbine, a condenser and a condensate pump.
  • the evaporators are basically connected in series.
  • a turbine comprising its own housing with a nozzle system and blade wheels.
  • These turbines are regrouped in pairs, wherein the blade wheels of a turbine pair have a common shaft.
  • the parallel shafts of two turbine pairs are interconnected by a gear system to drive an electrical generator.
  • the system comprises two evaporators associated with a two-stage turbine.
  • This two-stage turbine comprises a rotor carrying two axially spaced blade rings, wherein the first blade ring has a smaller diameter than the second blade ring.
  • a first steam flow i.e. high pressure steam produced by a high pressure evaporator
  • a second steam flow (low pressure steam produced by a low pressure evaporator) radially enters into the turbine housing through a low pressure inlet and flows through a second annular steam channel into a second nozzle ring, which deflects the flow in an axial direction into the second blade ring, i.e. the blade ring with the bigger diameter.
  • the two stages are designed so as to achieve the same end pressure at the outlet of the first and second blade ring, wherein the exhaust streams are only merged in an outlet diffuser of the turbine. It is obvious that such a turbine has a rather low efficiency, when compared e.g. to a typical induction type turbine, i.e.
  • turbo-machines generally axial flow turbines
  • displacement type machines most often derived from existing frigorific compressors
  • Examples of displacement type machines used in ORCs at lower power ranges are e.g.: reciprocating piston machines, volumetric spiral turbines (also called scroll turbines) and screw-type machines. All these displacement type machines have a poor efficiency and generally involve lubrication problems. Furthermore, displacement type machines often cause problems due to a limited tightness.
  • ORC For making power generation with an ORC in the kW-range a really interesting solution, it would be interesting to implement the ORC in a “black box”, i.e. a preassembled ORC circuit that is integrated in a closed container and ready to be connected to the heat carrier fluid and the cooling fluid.
  • a black box i.e. a preassembled ORC circuit that is integrated in a closed container and ready to be connected to the heat carrier fluid and the cooling fluid.
  • EP 1426565 A1 proposes e.g. an integrated thermal exchanger group for an ORC comprising a regenerator and a condenser, both arranged in a mainly cylindrical container with a horizontal axis.
  • DE 10 2008 038 241 A1 proposes a similar arrangement. These integrated heat exchangers still require that the turbine and the evaporator are installed as separate components.
  • U.S. Pat. No. 5,219,270 describes a recovery assembly for recovering energy from a wet oxidation.
  • the assembly comprises a bulky reaction barrel with rocket nozzles mounted in a vacuum chamber equipped with tubular cooling elements.
  • GB 1,027,223 describes a multi-stage turbine, wherein a separate condenser is associated with each turbine stage.
  • the turbine stages are axially spaced along a common shaft.
  • Each turbine stage discharges the expanded vapour directly into a chamber containing its separate condenser. The turbine itself is not further described.
  • a device for power generation according to a Rankine cycle (RC), in particular according to an organic Rankine cycle (ORC), comprises a turbine for expanding a vapour of a working fluid and at least one heat exchanger, such as a regenerator and/or a condenser, through which the expanded vapour has to flow.
  • the device further comprises a vapour tight container containing the turbine and the at least one heat exchanger.
  • the turbine is a radial-outward-flow type turbine having: a shaft that is led in a sealed manner out of the container; an axial vapour inlet port arranged opposite the shaft so as to be located inside the container; and a stator exhaust ring with stator exhaust blades defining peripheral vapour exhaust openings for discharging the expanded vapour directly into the vapour tight container, in which the expanded vapour flows through the at least one heat exchanger.
  • the invention combines in a very efficient way, a very compact, but very efficient radial-outward-flow type turbine and at least one heat exchanger, which is to be traversed by the vapour expanded in the turbine, in a common vapour tight containment.
  • the axial vapour inlet port is hereby arranged opposite the shaft and located inside the container, where it can be very easily connected to an internal vapour generator.
  • the direct peripheral expanded vapour discharge through the stator exhaust ring with its stator exhaust blades into the common container substantially reduces pressure losses between the turbine and the at least one heat exchanger.
  • the common container also reduces the risk of (organic) vapour losses to the atmosphere.
  • the container has the form of a vertical cylinder with a top end and a bottom end.
  • the turbine is advantageously centred in the top end of the container, and the at least one heat exchanger is located below the turbine. It will be appreciated that this design provides ideal flow conditions for the expanded vapour between the exhaust of the turbine and the at least one heat exchanger.
  • a preferred embodiment of the turbine is a radial-outward-flow type multi-stage turbine with vapour induction in at least one intermediary stage.
  • an annular vapour inlet port advantageously surrounds the axial vapour inlet port, and is arranged in the turbine so as to annularly induce, in an intermediary stage of the turbine, a vapour stream from a second evaporator into an already partially expanded vapour stream from a first evaporator.
  • the proposed radial-outward-flow type, multi-stage turbine can be very easily configured as an induction type turbine, wherein the manufacturing costs for the induction type turbine are not much higher than for a turbine with a single vapour inlet.
  • the device further includes a first evaporator and, optionally, a second evaporator.
  • the first evaporator and, if present, the second evaporator are advantageously arranged in the container, axially below the axial vapour inlet port of the turbine.
  • the at least one heat exchanger is then advantageously arranged annularly around the first evaporator and, if the second evaporator is present, annularly around the first and second evaporator.
  • the device gets particularly compact.
  • the intergration of the evaporator(s) into a common container with the turbine and at least one heat exchanger located downstream of the turbine further reduces the risk of (organic) vapour losses to the atmosphere.
  • Arranging the the evaporator(s) axially below the axial vapour inlet port of the turbine also allows to reduce pressure and heat losses between the evaporator(s) and the turbine.
  • the evaporator that is arranged in the common container may also be a vapour generator comprising an internal heat source, e.g. a novel type of low temperature heat source, which is based on chemical or nuclear reactions.
  • a preferred embodiment of the device further comprises a first vapour drum that is located in axial extension of the axial vapour inlet port and directly connected to the latter without any intermediate piping.
  • this embodiment further comprises a second vapour drum that is located in axial extension of the annular vapour inlet port and directly connected to the latter without any intermediate piping.
  • the second vapour drum is a compartment inside the first vapour drum, or the first vapour drum is a compartment inside the second vapour drum.
  • the axial vapour inlet port is advantageously formed by a first tubular vapour inlet connection, which is engaged in a sliding and sealed manner by the first vapour drum; and the annular vapour inlet port, if present, is advantageously formed by a second tubular vapour inlet connection surrounding the first tubular vapour inlet connection, wherein the second tubular vapour inlet connection is advantageously engaged in a sliding and sealed manner by the second vapour drum.
  • first vapour drum and/or the second vapour drum are advantageously supported by the first evaporator and/or second evaporator or by a support structure associated with the first evaporator and/or second evaporator.
  • Such combined low and high pressure vapour drums which are connected without any intermediate piping and, preferably, with sliding connections to the turbine vapour inlets, reduce pressure losses at the vapour inlet(s) of the turbine, allow to easily achieve a superheating of the low pressure vapour by the high pressure vapour, thereby increasing efficiency of the Rankine cycle, make the device more compact, facilitate its assembling and reduce its costs.
  • the at least one heat exchanger includes a first regenerator that is arranged in the container so that the exhaust vapour of the turbine flows directly through it; this first regenerator being connected to a fluid inlet port of a first evaporator, so as to reheat the fluid with heat extracted from the exhaust vapour flowing through the first regenerator.
  • the at least one heat exchanger may further include a second regenerator that is arranged in the container so that the vapour having crossed the first regenerator flows through it; this second regenerator being connected to a fluid inlet port of a second evaporator, so as to reheat the fluid with heat extracted from the vapour flowing through the second regenerator.
  • the at least one heat exchanger may also include a condenser in which the expanded vapour is condensed, wherein, if present, the first regenerator, the second generator and the condenser are arranged below the turbine, vertically one above the other.
  • This configuration is not only very compact. It also provides nearly ideal flow conditions for the vapour between the exhaust of the turbine, the regenerators and the condenser.
  • the device further includes a first evaporator connected to an axial vapour inlet port of the turbine, a second evaporator working at a lower evaporation pressure than the first evaporator and connected to an annular vapour inlet port of the turbine for inducing lower pressure vapour into an intermediary stage of the turbine; for the first evaporator, a first heat carrier fluid inlet port and a first heat carrier fluid outlet port; for the second evaporator, a second heat carrier fluid inlet port and a second heat carrier fluid outlet port; a connection pipe connecting the first heat carrier fluid outlet port to the second heat carrier fluid inlet port; and optionally, a bypass-valve connected between the second heat carrier fluid inlet port and the second heat carrier fluid outlet port, for adjusting the flow rate of the heat carrier fluid in the second evaporator.
  • a first evaporator connected to an axial vapour inlet port of the turbine, a second evaporator working at a lower evaporation pressure than the first evaporator and connected to
  • the at least one heat exchanger includes a condenser, and a condensate collector is arranged under the condenser in the container.
  • a condensate outlet port is advantageously connected to the condensate collector;
  • a first condensate inlet is advantageously connected either directly or through a first regenerator to a first evaporator;
  • a second condensate inlet is advantageously connected, either directly or through a second regenerator, to a second evaporator;
  • a condensate pump is advantageously connected with its suction side to the condensate collector, and with its pressure side via a first valve to the first condensate inlet and via a second valve to the second condensate inlet.
  • the device includes an air-cooled condenser arranged outside the container connected to the container by means of a large diameter vapour pipe.
  • the at least one heat exchanger then includes at least one regenerator arranged in the container so that the expanded vapour flows through it before being channelled through the large diameter pipe into the air-cooled condenser. It will be appreciated that even with an external air-cooled condenser, the device can remain very compact.
  • a preferred embodiment of the turbine comprises: a substantially plate-shaped first turbine housing part including the axial vapour inlet port; a set of stator rings with stator blades, the stator rings having increasing diameters and being preferably fixed with screws onto the first turbine housing part; a stator exhaust ring with stator exhaust blades, the stator exhaust ring radially surrounding the stator ring with the biggest diameter and being preferably fixed with screws onto the first turbine housing part, the stator exhaust blades defining the vapour exhaust openings for discharging the expanded vapour into the container; a substantially plate-shaped second turbine housing part including a shaft outlet neck; the second turbine housing part being preferably fixed with screws onto the stator exhaust ring; a turbine shaft rotatably supported within the shaft outlet neck; a rotor disk supported in a cantilever manner by the turbine shaft between the first turbine housing part and the second turbine housing part; for each stator ring, a rotor ring with rotor blades, the rotor ring radially surrounding the corresponding stator
  • the turbine advantageously includes an annular vapour inlet port formed in the first turbine housing part as a ring-zone with through-holes, the ring-zone separating a first ring-shaped flange, which supports a first set of stator rings, from a second ring-shaped flange, which supports a second set of stator rings.
  • a vapour induction port may thus be added to the turbine with very simple means and at very low costs.
  • the turbine is an induction turbine comprising: a first turbine housing part including the axial vapour inlet port; a set of stator rings with stator blades supported by the first turbine housing part; a turbine shaft supporting in a cantilever manner a rotor disk; for each stator ring, a rotor ring with rotor blades, the rotor ring radially surrounding the corresponding stator ring and being supported by the rotor disk; an annular vapour inlet port formed in the first turbine housing part as a ring-zone with through-holes.
  • These through-holes advantageously open onto an outer rim of one of the rotor rings, this outer rim having a width decreasing towards its periphery, and forming an annular, preferably concave, surface, which defines with an annular, preferably convex, surface on the next stator ring, a ring-shaped converging nozzle, for annularly inducing, into the next stator ring, a vapour stream from the through-holes into a vapour stream flowing through the preceding rotor ring.
  • vapour induction is fluidically optimized at relatively low costs.
  • the first turbine housing part supports an end-cap, which forms a vapour inlet deflection surface opposite the axial vapour inlet port; this vapour inlet deflection surface being a revolution surface centred on the central axis of the turbine; wherein a first stator ring is integrated into the end-cap.
  • the second turbine housing part is mounted in a sealed manner in an opening of the container, so that a shaft outlet neck of the second turbine housing part is located outside the container.
  • the turbine advantageously further includes: rolling contact bearings in the shaft outlet neck for supporting and locating the turbine shaft therein; and a shaft sealing device located adjacent to the rolling contact bearings, so that the rolling contact bearings are sealed from the vapour in the turbine.
  • the shaft bearings may be rather standard rolling contact bearings, which are easily accessible outside the common container for monitoring and maintenance purposes.
  • FIG. 1 is a block diagram schematically illustrating how different components of a preferred device for power generation according to an improved organic Rankine cycle (ORC) are interconnected;
  • ORC organic Rankine cycle
  • FIG. 2 is a schematic sectional view of a multi-stage turbine, in which low pressure vapour is induced at a low pressure turbine stage, the section plane containing the central axis of the turbine;
  • FIG. 3 is an enlarged detail of FIG. 2 ;
  • FIG. 4 is a schematic sectional view of a turbine as shown in FIG. 2 , the section plane being this time perpendicular to the central axis of the turbine;
  • FIG. 5 is a schematic sectional view of the turbine as in FIG. 2 , further schematically showing a first arrangement of a high pressure vapour drum and a low pressure vapour drum directly connected to the turbine;
  • FIG. 6 is a schematic sectional view as in FIG. 5 , showing a slightly modified embodiment
  • FIG. 7 is a schematic sectional view as in FIG. 5 , showing a further possibility how to connect the high pressure vapour drum and the low pressure vapour drum to the turbine;
  • FIG. 8 is a schematic sectional view as in FIG. 5 , showing an additional possibility how to connect the high pressure vapour drum and the low pressure vapour drum to the turbine;
  • FIG. 9 is a schematic sectional view of a device in accordance with the invention, the section plane being a vertical plane;
  • FIG. 10 is a schematic sectional view of as indicated by line 9 - 9 ′ in FIG. 9 ;
  • FIG. 9 is a schematic sectional view of a device in accordance with the invention, which is equipped with an air cooled condenser.
  • FIG. 1 is a block diagram schematically illustrating how different components of device for power generation according to an improved Organic Rankine Cycle (ORC) are interconnected.
  • This device comprises following main components arranged within a closed vapour tight container 10 : a first or high pressure evaporator 12 , a second or low pressure evaporator 14 ; a turbine 16 ; a condenser 18 and two regenerators 20 , 22 . It further comprises a condensate pump 24 and an electrical generator 26 , which are preferably arranged outside of the container 10 .
  • the preferred device comprises moreover following fluid inlet and outlet ports:
  • Reference number 42 identifies an external heat transfer circuit, associated e.g. with a low temperature external heat source.
  • this external heat transfer circuit 42 circulates a heat carrier fluid, such as a heat-transfer-oil, which transports the heat energy to be transformed by the ORC in mechanical energy.
  • the heat carrier fluid enters through the first heat carrier fluid inlet port 30 into the first evaporator 12 , traverses the latter, thereby heating and evaporating an organic working fluid flowing through the first evaporator 12 . Thereafter, the heat carrier fluid leaves the container 10 through the first heat carrier fluid outlet port 30 ′, to be channelled through an external connection conduit 44 to the second heat carrier fluid inlet port 32 .
  • the heat carrier fluid enters into the second evaporator 14 , traverses the latter, thereby heating and evaporating the organic working fluid flowing through the second evaporator 14 . Thereafter, the heat carrier fluid definitively leaves the container 10 through the second heat carrier fluid outlet port 32 ′.
  • the external connection conduit 44 it is possible to foresee an internal connection conduit (not shown) located within the container 10 , which would eliminate the first heat carrier fluid outlet port 30 ′ and the second heat carrier fluid inlet port 32 .
  • the solution with the external first heat carrier fluid outlet port 30 ′ and the second heat carrier fluid inlet port 32 warrants a greater flexibility.
  • a bypass-valve 45 is moreover connected between the second heat carrier fluid inlet and outlet ports 32 , 32 ′.
  • This bypass-valve 45 allows limiting the flow of heat carrier fluid through the second evaporator 14 , thereby limiting the At of the heat carrier fluid between the ports 30 and 32 ′.
  • the organic fluid vapour produced in the first evaporator 12 is channelled into a high pressure vapour drum 46 , which is directly, i.e. without any intermediate piping, connected to a high pressure inlet of the turbine 16 .
  • the organic vapour produced in the second evaporator 14 which has a lower pressure than the organic vapour produced in the first evaporator 12 and is therefore called low pressure vapour, is channelled into a low pressure vapour drum 48 , which is directly, i.e. without any intermediate piping, connected to a low pressure inlet of the turbine 16 .
  • both vapour streams are expanded to generate a torque for driving the generator 26 coupled to the turbine 16 .
  • the ORC cycle is generally designed so that the vapour at the turbine exhaust has not yet reached a two-phase state (to achieve this aim the organic fluid should preferably be a “dry” ORC working fluid, i.e. it should have a positive or isentropic saturation vapour curve). It follows that the temperature of the vapour at the outlet of the turbine 16 is still much higher than the condensing temperature in the condenser 18 . In the two regenerators 20 and 22 , this temperature difference is efficiently used to preheat the condensate before it enters into evaporator 12 or 14 .
  • the first regenerator 20 which is heated directly with the exhaust vapour of the turbine 16 , preheats the condensate stream pumped through the first evaporator 12 , which works at a higher pressure and consequently also with a higher evaporating temperature than the second evaporator 14 .
  • the second regenerator 22 which is heated with the vapour already cooled down in the first regenerator 20 , preheats the condensate stream pumped through the second evaporator 14 , which works at a lower evaporating temperature. It will be appreciated that this two-stage regeneration allows a more efficient heat exchange in the regenerators 20 , 22 and the evaporators 12 , 14 than a single-stage regeneration.
  • the organic working fluid is condensed by means of an external cooling circuit 50 connected to the cooling fluid inlet port 34 and outlet port 34 ′ of the condenser 18 .
  • an external cooling circuit 50 may e.g. comprise a dry or a wet cooling tower (not shown).
  • the condensate pump 24 pressurizes the condensed organic working fluid collected at the condenser 18 and pumps it through the regenerators 20 , 22 to the two evaporators 12 , 14 . More particularly, at the outlet of the condensate pump 24 , the pressurized condensate is split in two separate condensate streams.
  • a first condensate stream is pumped through a first valve 52 , which is connected to the first condensate inlet port 38 . This first condensate stream flows through the first regenerator 20 , wherein it is pre-heated by the exhaust vapour of the turbine 16 , into the first evaporator 12 .
  • a second condensate stream is pumped through a second valve 54 , which is connected the second condensate inlet port 40 .
  • This second condensate stream flows through the second regenerator 22 , wherein it is pre-heated by the expanded vapour, into the second evaporator 14 .
  • the first and second valve 52 , 54 allow to adjust the pressures in the evaporator 12 and 14 independently from one another.
  • two separate condensate pumps can be used, one for pumping the first condensate flow through the first regenerator 20 into the first evaporator 12 , and the other for pumping the second condensate flow through the second regenerator 22 into the second evaporator 14 .
  • the efficiency of this two-stage ORC is about 15% for a ⁇ t of 100° C., but about 11% of the available energy in the heat carrier fluid is converted into mechanical energy. Without the low pressure circuit (i.e. without the second evaporator 14 , the second regenerator 22 , the low pressure vapour drum 48 and the low pressure vapour inlet of the turbine 16 ), the efficiency of the single stage ORC would be about 21%, but only about 7% of the available energy in the heat carrier fluid would be converted into mechanical energy.
  • Typical temperature ranges for the heat carrier fluid are e.g.:
  • Inlet temperature of the heat carrier fluid 140° C. to 350° C.
  • Outlet temperature of the heat carrier fluid 66 to 150° C.
  • the circuit of FIG. 1 only comprises the first regenerator 20 , i.e. the second condensate inlet port 40 is directly connected to the second evaporator 14 , without passing by a regenerator.
  • the first condensate inlet port 40 is directly connected to the first evaporator 14
  • the second condensate inlet port 40 is directly connected to the second evaporator 14 , without passing by a regenerator.
  • the circuit comprises in addition to the high pressure evaporator 12 more than one low pressure evaporator, each of these low pressure evaporators supplying the turbine 16 with vapour at a different intermediate pressure, which is induced into the turbine at a stage in which the pressure of the expanded vapour is about equal to the pressure of the induced vapour.
  • a regenerator can be associated with each evaporator or only with one or more selected evaporators.
  • FIG. 2 is a schematic cross-section through an embodiment of the turbine 16 that is particularly suited for being used in an ORC as described above.
  • the turbine 16 is a multi-stage (here a three-stage) radial-outward-flow type turbine, i.e. the vapour axially enters into the turbine 16 and then flows in a radial direction outward through the different stages of the turbine 16 , which are substantially concentric.
  • the turbine is furthermore of the induction type, i.e. a secondary flow of low pressure vapour is induced at a low pressure stage into the turbine 16 .
  • the turbine is of the impulse type, i.e. the vapour is mainly expanded as it passes through the stator of the turbine 16 .
  • each of the three turbine stages comprises a stator ring 56 1 , 56 2 , 56 3 , with increasing diameter and curved stator blades 58 1 , 58 2 , 58 3 , and a rotor ring 60 1 , 60 2 , 60 3 , with increasing diameter and curved rotor blades 62 1 , 62 2 , 62 3 .
  • the inlet stator ring 56 1 and the first rotor ring 60 1 form the first stage of the turbine 16 .
  • the second stator ring 56 2 and the second rotor ring 60 2 form the second stage of the turbine 16 .
  • the third stator ring 56 3 and the third rotor ring 60 3 form the third stage of the turbine 16 .
  • a fourth ring 56 4 surrounds the third or last stage of the turbine 16 , to form a stator exhaust ring 56 4 , with stator exhaust blades 58 4 .
  • the turbine 16 may also be designed with 4 stages or more, by adding one or more pairs of stator and rotor rings.
  • the rotor rings 60 1 , 60 2 , 60 3 are supported by a rotor disk 64 , which is fixed to a free end of a turbine shaft 66 .
  • the turbine shaft 66 with the rotor disk 64 is rotatably supported in a cantilever fashion in a shaft outlet neck 72 by means of a bearing arrangement, preferably built up with rolling contact bearings.
  • Reference number 68 points to a schematic representation of such a rolling contact bearing.
  • Reference number 70 identifies a schematic representation of a sealing device, which seals the shaft 66 in the shaft outlet neck 72 , between the rotor disk 64 and the bearing arrangement.
  • Reference number 74 identifies the central axis of the turbine shaft 66 , which is also the central axis of all rotor rings 60 1 , 60 2 , 60 3 (and of all stator rings 56 1 , 56 2 , 56 3 , 56 4 ), since all these rings are coaxial with the turbine shaft 66 .
  • the rotor disk 64 is axially secured to the turbine shaft 66 , e.g. by means of a nut 75 or a screw (not shown), and that the torque is transmitted from the rotor disk 64 to the turbine shaft 66 by means of a form-fit or keyed assembly (not shown).
  • the rotor rings 60 1 , 60 2 , 60 3 are fixed with screws 76 to the rotor disk 64 , so that they are easily exchangeable.
  • the stator rings 56 1 , 56 2 , 56 3 are fixed with screws 78 to a plate-shaped first turbine housing part 80 .
  • This first turbine housing part 80 comprises a first and a second tubular vapour inlet connection 82 , 84 , a first and a second ring-shaped flange 88 , 90 and a perforated ring zone 92 .
  • the first tubular vapour inlet connection 82 is centred on the central axis 74 of the turbine 16 .
  • the second tubular vapour inlet connection 84 surrounds the first tubular vapour inlet connection 82 , so as to define with the latter an annular space 86 , wherein the perforated ring zone 92 is contained in this annular space 86 .
  • the first ring-shaped flange 88 forms a shoulder around the first tubular vapour inlet connection 82 .
  • the second ring-shaped flange 90 forms a shoulder around the second tubular vapour inlet connection 84 .
  • the perforated ring zone 92 joins the first flange 88 and the second ring-shaped flange 90 and is provided with through-holes 94 .
  • the first and/or second tubular vapour inlet connection 82 , 84 could also be flanged to the first turbine housing part 80 .
  • the first turbine housing part 80 mainly consists of the first ring-shaped flange 88 , the second ring-shaped flange 90 and the perforated ring zone 92 , which joins the first and the second ring-shaped flange 88 , 90 .
  • first ring-shaped flange 88 advantageously comprises a first connection means for flanging a removable first vapour inlet connection thereto
  • second ring-shaped flange 90 advantageously comprises a second connection means for flanging a removable second vapour inlet connection thereto (not shown in the drawings).
  • the first ring-shaped flange 88 supports the first and the second stator ring 56 1 , 56 2 .
  • the first stator ring 56 1 is advantageously part of an end-cap 96 , which forms a vapour inlet deflection surface 98 at the end of the first tubular vapour inlet connection 82 .
  • This vapour inlet deflection surface 98 is a revolution surface centred on the central axis 74 of the turbine 16 , so as to annularly deflect the axial vapour stream in the first tubular vapour inlet connection 82 by 90° into the first stator ring 56 1 .
  • the second ring-shaped flange 90 supports the third stator ring 56 3 , as well as the exhaust stator ring 56 4 .
  • the first turbine housing part 80 is fixed to a plate-shaped second turbine housing part 100 .
  • the rotor disk 64 with the rotor rings 60 1 , 60 2 , 60 3 is hereby located axially between the first housing part 80 and the second housing part 100 .
  • the first rotor ring 60 1 is located between the first and the second stator ring 56 1 and 56 2 ; the second rotor ring 60 2 is located between the second and the third stator ring 56 2 and 56 3 ; and the third rotor ring 60 3 is located between the third stator ring 56 3 and the exhaust stator ring 56 4 .
  • the height of the stator blades 58 1 , 58 2 , 58 3 and rotor blades 62 1 , 62 2 , 62 3 can be modified, by simply exchanging the removable stator rings 56 and rotor rings 60 .
  • a broad electric power range may be covered by simply changing the height of the rotor and stator blades 58 , 62 , all other geometric characteristics of the rotor and stator rings 56 , 60 and blades 58 , 62 remaining unchanged. Furthermore, if the available heat energy increases or decreases during lifetime of the turbine, the latter may be easily reconfigured for the new operating conditions by simply exchanging its rotor and stator rings 56 , 60 .
  • each of the three stator rings 56 1 , 56 2 , 56 3 includes at its base an annular shoulder 102 1 , 102 2 , 102 3 , which forms a labyrinth joint 10 6 with an opposite grooved surface located on an annular outer rim 104 1 , 104 2 , 104 3 of the corresponding rotor ring 60 1 , 60 2 , 60 3 .
  • each of the first two rotor rings 60 1 , 60 2 includes at its base an annular shoulder 108 1 , 108 2 , which forms a labyrinth joint 112 with an opposite grooved surface located on an annular outer rim 110 2 , 110 3 of the corresponding stator ring 56 2 , 56 3 .
  • vapour tightness in the radial direction between the rotating and stationary parts is solely achieved by easily machinable surfaces on the removable stator rings 56 1 , 56 2 , 56 3 and rotor rings 60 1 , 60 2 , and necessitates neither complicated machining on the turbine housing parts 80 , 100 or the rotor disk 64 , nor separate sealing elements.
  • the removable stator rings 56 1 , 56 2 , 56 3 and rotor rings 60 1 , 60 2 may be designed without the aforementioned annular shoulder, wherein the outer rims 104 1 , 104 2 , 104 3 of the rotor rings 60 1 , 60 2 , 60 3 and the outer rims 110 2 , 110 3 of the stator rings 56 2 , 56 3 cooperate directly with corresponding annular surfaces on the housing part 80 and the rotor disk 64 to form labyrinth joints.
  • annular shoulder 102 2 of the second stator ring 56 2 is smaller than the other two annular shoulders 102 1 , 102 3 , thereby leaving uncovered the through-holes 94 in the perforated ring zone 92 of the first turbine housing part 80 .
  • the width of the annular outer rim 104 2 of the second rotor ring 60 2 which is located just behind the perforated ring zone 92 , decreases towards its periphery, so as to define with the opposite surface of the third stator ring 56 3 a ring-shaped converging nozzle 114 , which is delimited, on one side, by an annular concave surface 116 defined by the second rotor ring 60 2 and, on the other side, by an annular convex surface 118 defined by the third stator ring 56 3 .
  • This ring-shaped nozzle 114 deflects the low pressure vapour stream, which flows from the annular space 86 in an axial direction through the through-holes 94 , by an angle of 90° into the third stator ring 56 3 .
  • this low pressure vapour stream is induced into the main vapour stream that has already been expanded in the first and second stage of the turbine 16 , so that both vapour streams have substantially the same pressure when they merge in the third stator ring 56 3 .
  • the expansion of the vapour in the second stator ring 56 2 and the third stator ring 56 3 is mainly achieved by increasing the height of the stator blades 58 in the radial direction (i.e. the height of these blades at the outlet is considerably higher than their height at the inlet of the stator ring).
  • the expansion of the vapour in these stator rings 56 2 and 56 3 is mainly determined by the increasing height of their blades. Consequently, for adapting the turbine to a different vapour throughput or a different inlet pressure in the turbine 16 , it will not be necessary to entirely change the geometry of the rotor or stator blades 58 , 62 . It will most often simply be sufficient to change the height of the rotor and stator blades 58 , 62 , all other geometric characteristics of the rotor and stator rings 56 , 60 and blades 58 , 62 remaining basically unchanged.
  • the turbine as described hereinbefore may achieve an isentropic efficiency as high as 90%. Its rotation speed will preferably be limited to 18,000 rpm, so to be capable of working with rolling contact bearings and common shaft sealing devices.
  • FIG. 5 schematically shows a first arrangement of the high pressure vapour drum 46 and the low pressure vapour drum 48 , both directly located under the turbine 16 and directly connected to latter without any intermediate piping.
  • the high pressure vapour drum 46 is a cylindrical vessel directly flanged to the first turbine housing part 80 .
  • the low pressure vapour drum 48 forms an annular compartment within the high pressure vapour drum 46 . This annular compartment is outwardly delimited by a cylindrical external wall 120 of the high pressure vapour drum 46 and inwardly delimited by a cylindrical internal wall 122 .
  • This cylindrical internal wall 122 engages the first tubular vapour inlet connection 82 of the turbine 16 in a sealed fit, wherein this sealed fit shall however be designed (e.g.
  • Reference number 124 points to a high pressure vapour inlet pipe connected laterally to the high pressure vapour drum 46
  • reference number 126 points to a low pressure vapour inlet pipe connected laterally to the low pressure vapour drum 48 .
  • FIG. 6 distinguishes over the arrangement of FIG. 5 mainly in that the low pressure vapour inlet pipe 126 ′ traverses the high pressure vapour drum 46 to leave the latter through its bottom wall.
  • This design necessitates that the low pressure vapour inlet pipe 126 and the high pressure vapour drum 46 may freely expand relative to one another. This can e.g. be achieved by connecting the low pressure vapour inlet pipe 126 by means of a bellow expansion joint (not shown) to the closed end of the high pressure vapour drum 46 .
  • FIG. 7 shows a further arrangement of the high pressure vapour drum 46 and the low pressure vapour drum 48 connected to the turbine 16 .
  • the low pressure vapour drum 48 is a cylindrical vessel flanged to the first turbine housing part 80 .
  • the high pressure vapour drum 46 forms a cylindrical compartment within the low pressure vapour drum 48 , separated from the outer wall of the latter by an annular space 130 . It is vertically supported by a support flange 132 , which is welded into the low pressure vapour drum 48 .
  • Through-openings 134 in the support flange 132 allow the intermediate pressure vapour to pass from an inlet compartment 136 of the low pressure vapour drum 48 into the annular space 130 .
  • the high pressure vapour drum 46 engages the first tubular vapour inlet connection 82 of the turbine 16 in a sealed way, wherein this sealed fit shall however be designed (e.g. with O-rings) to allow relative axial movement of the high pressure vapour drum 46 and the first tubular vapour inlet connection 82 .
  • this sealed fit shall however be designed (e.g. with O-rings) to allow relative axial movement of the high pressure vapour drum 46 and the first tubular vapour inlet connection 82 .
  • the passage of the pipe 124 through the bottom wall of the low pressure vapour drum 48 is designed for allowing a relative axial expansion of both components.
  • the outer vessel is flanged to the first turbine housing part 80 of the turbine 16 , and must consequently be able to axially expand away from the turbine 16 .
  • the outer vessel 140 is no longer flanged to the first turbine housing part 80 of the turbine 16 . It simply engages the second tubular vapour inlet connection 84 of the turbine 16 in a sealed way, wherein this sealed fit is designed (e.g. with O-rings) to allow a relative axial movement of the outer vessel 140 and the second tubular vapour inlet connection 84 .
  • the outer vessel 140 (which may be the high pressure vapour drum 46 as in FIG.
  • the outer vessel 140 may e.g. be directly supported on the first or second evaporator 12 , 14 , when the latter are axially arranged under the outer vessel 140 . It will consequently be appreciated that in the embodiment of FIG. 7 , the turbine 16 must not support the whole weight of the two vapour drums 46 , 48 .
  • the low pressure vapour is slightly superheated by contact with one or more walls of the high pressure vapour drum 46 , which may be advantageous for the efficiency of the low pressure cycle.
  • This superheating-effect is more important for the embodiment of FIG. 7 and may be further amplified by providing the outer wall of the inner cylinder 46 in FIG. 7 with fins.
  • FIGS. 9 and 10 show a compact device for electric power generation according to an improved ORC, more particularly, to an ORC working with two evaporators 12 , 14 , two regenerators 20 , 22 and an induction turbine 16 , so as illustrated with the circuit of FIG. 1 .
  • the container 10 is a vertical vapour tight cylinder supported on support feet 150 .
  • the turbine 16 is located inside the vertical cylinder 10 , near the top end of the latter.
  • the central axis 74 of the turbine is aligned with the central axis of the container 10 .
  • the second turbine housing part 100 is fixed with in a sealed manner to a head-plate 152 , which is a part of the upper container wall.
  • the second turbine housing part 100 may include an annular flange (not shown) with which it is fixed in a sealed manner onto a flange surrounding an axial opening (not shown) in the head of the container 10 .
  • a generator 154 is arranged on the top of the vertical cylinder 10 and is coupled to the vertical shaft of the turbine 16 . It will be appreciated that with this arrangement, the bearing arrangement 68 of the turbine shaft 66 is located completely outside the container 10 , which greatly facilitates the design of its lubrication system, but also its maintenance.
  • the high pressure vapour drum 46 and the low pressure vapour drum 48 are arranged axially directly under the turbine 16 . Both vapour drums 46 , 48 are advantageously connected to the first and second tubular vapour inlet connection 82 , 84 of the turbine 16 as described e.g. with reference to FIG. 5 or 6 and FIG. 8 .
  • the first evaporator 12 and the second evaporator 14 are arranged axially directly under the two vapour drums 46 , 48 , which can be vertically supported by the two evaporators 12 , 14 , as described with reference to FIG. 8 . These two evaporators 12 , 14 are preferably enclosed in a separate cylindrical compartment 156 .
  • the first and second regenerator 20 , 22 are arranged annularly around the two vapour drums 46 , 48 , wherein the second regenerator 22 is arranged directly under the first regenerator 20 .
  • the condenser 18 is arranged annularly around the two evaporators 12 , 14 .
  • the bottom part of the vertical cylinder 10 forms a condensate collector 158 .
  • the turbine 16 which is preferably conceived substantially as described hereinbefore, radially discharges the expanded vapour through the stator exhaust ring 56 4 directly into the upper part of the vertical cylinder 10 .
  • An annular deflector (not shown) may be used to deflect the radially discharged vapour axially downwards. This annular deflector may be incorporated into the turbine 16 or be installed as a separate element into the container 10 .
  • the expanded vapour then passes downwards through the first and second regenerator 20 , 22 , to be finally condensed in the condenser 18 .
  • the condensate is collected in the condensate collector 158 at the bottom of the vertical cylinder 10 .
  • the pipe connections 30 , 30 ′, 32 , 32 ′, 34 , 34 ′, 36 and 38 shown in FIG. 9 correspond to the inlet/outlet ports with the same reference numbers shown in FIG. 1 .
  • FIG. 10 is a horizontal cross-section of the device shown in FIG. 9 .
  • This FIG. 10 shows that the annular heat-exchangers 18 , 20 , 22 do not occupy the whole annular space around the separate cylindrical compartment 156 in which the evaporators 12 , 14 are arranged.
  • the free space here an angular segment of about 40°, is used for arranging therein piping and auxiliary equipment, which is only schematically represented in FIG. 10 and identified therein with reference number 160 .
  • FIG. 11 shows an alternative embodiment with an air-cooled condenser 170 installed outside the container 10 , which still contains the evaporators 12 , 14 , the regenerators 20 , 22 , the vapour drums 46 , 48 , and the turbine 16 , which are advantageously arranged in this container 10 as described hereinbefore with reference to FIG. 9 .
  • the bottom half of the container 10 which was occupied by the condenser 18 in the embodiment of FIG. 9 , is now empty and connected via a large diameter pipe 172 to the air-cooled condenser 170 .
  • the latter includes a central chimney 174 with a closed end 176 , which is connected to at least one upper vapour collector 178 .
  • the vapour streams through at least one air-cooled condensing heat exchanger 180 , which condenses the vapour.
  • the condensate is collected in at least one lower condensate collector 182 and evacuated back into the condensate collector 158 in the container 10 through a condensate line 184 .
  • Condensate that is already formed in the central chimney 174 flows back into the condensate collector 158 in the container 10 through the large diameter pipe 172 .
  • Reference number 186 identifies a fan for creating an air flow 188 through the condensing heat exchanger(s) 180 and along the outer wall of the chimney 174 , which may be equipped with cooling fins too.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
US14/390,284 2012-04-03 2013-04-02 Device for power generation according to a rankine cycle Abandoned US20150082793A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP12163019 2012-04-03
EP12163019.8 2012-04-03
PCT/EP2013/056918 WO2013150018A2 (fr) 2012-04-03 2013-04-02 Dispositif de génération de puissance en fonction d'un cycle de rankine

Publications (1)

Publication Number Publication Date
US20150082793A1 true US20150082793A1 (en) 2015-03-26

Family

ID=48141924

Family Applications (1)

Application Number Title Priority Date Filing Date
US14/390,284 Abandoned US20150082793A1 (en) 2012-04-03 2013-04-02 Device for power generation according to a rankine cycle

Country Status (4)

Country Link
US (1) US20150082793A1 (fr)
EP (1) EP2834478A2 (fr)
CA (1) CA2869061A1 (fr)
WO (1) WO2013150018A2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020026022A1 (fr) 2018-07-30 2020-02-06 Ormat Technologies Inc. Système et procédé d'augmentation de la puissance de sortie par une turbine à vapeur organique

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITMI20120852A1 (it) 2012-05-17 2013-11-18 Exergy Orc S R L Sistema orc per la produzione di energia tramite ciclo rankine organico
EP3351724A4 (fr) * 2015-09-18 2019-05-15 Obshchestvo S Ogranichennoj Otvetstvennostyu "Turboenerdzhi" Procédé de conversion de l'énergie d'un milieu de travail gazeux et installation de mise en uvre
ITUA20163292A1 (it) 2016-05-10 2017-11-10 Turboden Srl Turbina a flusso misto ottimizzata
CN109667625A (zh) * 2019-02-01 2019-04-23 中国船舶重工集团公司第七0三研究所 一种用于可倒车涡轮鼓风损失试验的悬臂式转子
WO2024084359A1 (fr) * 2022-10-19 2024-04-25 Turboden S.p.A. Récupérateur à collecteurs externes pour installations à cycle organique de rankine

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4510757A (en) * 1984-01-03 1985-04-16 Graham Jr Merrill E Heat engine
US20040068975A1 (en) * 2002-07-29 2004-04-15 Skowronski Mark Joseph Kinetic energy turbine with recuperation
US20110115226A1 (en) * 2009-11-16 2011-05-19 General Electric Company Systems and apparatus relating to solar-thermal power generation
US20110120129A1 (en) * 2009-11-24 2011-05-26 General Electric Company Direct evaporator apparatus and energy recovery system
US20120009055A1 (en) * 2009-03-18 2012-01-12 Hk Turbine Co., Ltd. Reaction-type turbine
US20120125002A1 (en) * 2010-11-19 2012-05-24 General Electric Company Rankine cycle integrated with organic rankine cycle and absorption chiller cycle
US8336311B2 (en) * 2007-05-14 2012-12-25 Mitsubishi Heavy Industries, Ltd. Low-pressure-vapor-recovery turbine generator
US20140007575A1 (en) * 2010-08-11 2014-01-09 Cummins Intellectual Property, Inc. Split radiator design for heat rejection optimization for a waste heat recovery system
US20140099184A1 (en) * 2011-03-29 2014-04-10 Antonio Asti Sealing systems for turboexpanders for use in organic rankine cycles

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1027223A (en) 1962-06-25 1966-04-27 Ass Elect Ind Improvements in or relating to power plants
US4059961A (en) * 1975-12-10 1977-11-29 Parra M Rodolfo De Thermal motor of action and reaction forces
US5219270A (en) 1991-08-22 1993-06-15 Titmas And Associates Incorporated Reaction barrel with rocket nozzles in staggered alignment and connecting ducts of unequal length
ITBS20020102A1 (it) 2002-11-11 2004-05-12 Turboden Srl Gruppo di scambio termico integrato per turbine a vapore di fluido
DE102007044625A1 (de) 2006-09-22 2008-04-03 Frank Eckert Turbine zum Einsatz in ORC-Kreisprozessen
DE102007037889A1 (de) 2007-08-10 2009-02-12 Georg Albersinger Kraftmaschine und KWK-Vorrichtung
DE102008038241A1 (de) 2008-08-18 2010-02-25 Eckert, Frank Wärmetauschersystem für Rankine-Prozesse
WO2011145969A1 (fr) * 2010-05-20 2011-11-24 Aleksandr Alekseevich Pavlov Turbine
NO332899B1 (no) * 2010-10-05 2013-01-28 Tollef Lund Dampturbin

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4510757A (en) * 1984-01-03 1985-04-16 Graham Jr Merrill E Heat engine
US20040068975A1 (en) * 2002-07-29 2004-04-15 Skowronski Mark Joseph Kinetic energy turbine with recuperation
US8336311B2 (en) * 2007-05-14 2012-12-25 Mitsubishi Heavy Industries, Ltd. Low-pressure-vapor-recovery turbine generator
US20120009055A1 (en) * 2009-03-18 2012-01-12 Hk Turbine Co., Ltd. Reaction-type turbine
US20110115226A1 (en) * 2009-11-16 2011-05-19 General Electric Company Systems and apparatus relating to solar-thermal power generation
US20110120129A1 (en) * 2009-11-24 2011-05-26 General Electric Company Direct evaporator apparatus and energy recovery system
US20140007575A1 (en) * 2010-08-11 2014-01-09 Cummins Intellectual Property, Inc. Split radiator design for heat rejection optimization for a waste heat recovery system
US20120125002A1 (en) * 2010-11-19 2012-05-24 General Electric Company Rankine cycle integrated with organic rankine cycle and absorption chiller cycle
US20140099184A1 (en) * 2011-03-29 2014-04-10 Antonio Asti Sealing systems for turboexpanders for use in organic rankine cycles

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020026022A1 (fr) 2018-07-30 2020-02-06 Ormat Technologies Inc. Système et procédé d'augmentation de la puissance de sortie par une turbine à vapeur organique
EP3821112A4 (fr) * 2018-07-30 2022-03-30 Ormat Technologies Inc. Système et procédé d'augmentation de la puissance de sortie par une turbine à vapeur organique
US11542837B2 (en) 2018-07-30 2023-01-03 Ormat Technologies Inc. System and method for increasing power output from an organic vapor turbine

Also Published As

Publication number Publication date
WO2013150018A3 (fr) 2014-04-03
CA2869061A1 (fr) 2013-10-10
WO2013150018A2 (fr) 2013-10-10
WO2013150018A9 (fr) 2014-06-12
EP2834478A2 (fr) 2015-02-11

Similar Documents

Publication Publication Date Title
US20150082793A1 (en) Device for power generation according to a rankine cycle
US4227373A (en) Waste heat recovery cycle for producing power and fresh water
RU2578075C2 (ru) Устройство и способ выработки энергии посредством органического цикла ренкина
US20180313340A1 (en) Orc binary cycle geothermal plant and process
CN101253310B (zh) 旋转容积式蒸汽机
JP6261052B2 (ja) 有機ランキンサイクルによるエネルギ発生の為のｏｒｃシステム及び方法
US20120006024A1 (en) Multi-component two-phase power cycle
SE438709B (sv) Gasturbinanleggning
US20180258799A1 (en) A multistage evaporation organic rankine cycle
US8813500B2 (en) Combined heat exchanger expander mounting system
WO2015189718A1 (fr) Turbine et procédé d'expansion d'un fluide de travail
US9840915B2 (en) Turbine
CN104863642A (zh) 一种小流量涡轮膨胀机
CN214464426U (zh) 兆瓦级向心涡轮式中低温余热发电机组
WO2013064858A1 (fr) Procédé et appareil de conversion d'énergie thermique en énergie mécanique
US11391183B2 (en) ORC power generation apparatus
WO2016005834A1 (fr) Turbine et procédé d'expansion d'un fluide de travail avec saut d'enthalpie isentropique élevé
CN117072267A (zh) 一种两级径向流膨胀机orc梯级发电系统
CN112814749A (zh) 兆瓦级向心涡轮式中低温余热发电机组以及发电方法

Legal Events

Date Code Title Description
AS Assignment

Owner name: EQUITHERM S.A R.L., LUXEMBOURG

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:MAITREJEAN, LUC;REEL/FRAME:036830/0936

Effective date: 20151001

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION