US20130160449A1 - Cascaded organic rankine cycle system - Google Patents

Cascaded organic rankine cycle system Download PDF

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Publication number
US20130160449A1
US20130160449A1 US13/334,994 US201113334994A US2013160449A1 US 20130160449 A1 US20130160449 A1 US 20130160449A1 US 201113334994 A US201113334994 A US 201113334994A US 2013160449 A1 US2013160449 A1 US 2013160449A1
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Prior art keywords
cycle
working fluid
topping
fluid
bottoming
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Abandoned
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US13/334,994
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English (en)
Inventor
Frederick J. Cogswell
Bruce P. Biederman
Lili Zhang
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Raytheon Technologies Corp
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United Technologies Corp
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Application filed by United Technologies Corp filed Critical United Technologies Corp
Priority to US13/334,994 priority Critical patent/US20130160449A1/en
Assigned to UNITED TECHNOLOGIES CORPORATION reassignment UNITED TECHNOLOGIES CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ZHANG, LILI, BIEDERMAN, BRUCE P., COGSWELL, FREDERICK J.
Priority to SG2012075271A priority patent/SG191468A1/en
Priority to EP12195287.3A priority patent/EP2607635B8/de
Priority to CA2798770A priority patent/CA2798770C/en
Priority to CN201210561391.5A priority patent/CN103174475B/zh
Publication of US20130160449A1 publication Critical patent/US20130160449A1/en
Abandoned legal-status Critical Current

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    • 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
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/04—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled condensation heat from one cycle heating the fluid in another cycle

Definitions

  • the present disclosure relates generally to Organic Rankine Cycle (ORC) systems and, more particularly, to a cascaded organic Rankine cycle.
  • ORC Organic Rankine Cycle
  • the Organic Rankine Cycle is a vapor power cycle with an organic fluid refrigerant instead of water/steam as the working fluid.
  • the working fluid is heated in an “evaporator/boiler” by a source of waste or low quality heat.
  • the fluid starts as a liquid and ends up as a vapor.
  • the high-pressure refrigerant vapor expands in the turbine to produce power.
  • the low-pressure vapor exhausted from the turbine is condensed then sent back to the pump to restart the cycle.
  • the simple rankine cycle used for power generation follows the process order: 1) Adiabatic pressure rise through a pump; 2) Isobaric heat addition in a preheater, evaporator and superheater; 3) Adiabatic expansion in a turbine; and 4) Isobaric heat rejection in a condenser, although other cycle modifications are possible such as the addition of a vapor-to-liquid recuperator.
  • thermodynamic irreversibility in organic Rankine cycles is caused by the large temperature difference in the evaporator between the temperature of the waste heat stream and the boiling refrigerant. The higher the waste heat stream temperature the greater this irreversibility becomes.
  • One way to reduce this loss is to cascade two thermodynamic cycles together where a cycle operating at higher temperatures rejects heat to a cycle operating at lower temperatures.
  • a cascaded Organic Rankine Cycle (ORC) system includes a bottoming cycle in thermal communication with a topping cycle through a condenser/evaporator in which a bottoming cycle working fluid is first evaporated and then superheated and a topping cycle working fluid is first desuperheated and then condensed such that a percentage of total heat transfer from the topping cycle fluid that occurs during a saturated condensation is equal to or less than a percentage of total heat transfer to the bottoming cycle fluid that occurs during a saturated evaporation.
  • a method of operating a cascaded Organic Rankine Cycle (ORC) system in which a bottoming cycle is in thermal communication with a topping cycle which includes maintaining a percent saturation for a fluid in the topping cycle at less than a 40 percent saturation for a fluid in the bottoming cycle.
  • FIG. 1 is a schematic diagram of a cascaded organic rankine cycle with a topping cycle and a bottoming cycle
  • FIG. 2 is a TS-diagram for the bottoming cycle
  • FIG. 3 is a TS-diagram for the topping cycle
  • FIG. 4 is a plot of temperature profiles in the counter-flow heat exchangers of the de-superheating and then condensing topping fluid (Siloxane MM), and the evaporating and then superheating bottoming fluid (R245fa).
  • FIG. 1 schematically illustrates a cascaded Organic Rankine Cycle (ORC) system 20 .
  • the cascaded ORC system 20 includes at least two Rankine cycles, where a relatively hotter topping cycle 22 is cascaded with a relatively cooler bottoming cycle 24 .
  • the topping cycle 22 uses Siloxane MM as the working fluid while the bottoming cycle 24 uses R245fa. It should be appreciated, however, that additional cycles and other working fluids may additionally be utilized.
  • the topping cycle 22 generally includes a power producing turbine 26 which is driven by the working fluid to drive a generator 28 that produces power.
  • a refrigerant pump 30 increases the pressure of the working fluid from a condenser/evaporator 32 .
  • the heat exchanger group that transfers heat from the topping cycle 22 to the bottoming cycle 24 is referred to herein as the “condenser/evaporator” 32 , although it should be understood that it may also include desuperheating and subcooling of the working fluid in the topping cycle 22 , and preheating and superheating of the working fluid in the bottoming cycle 24 .
  • An evaporator 34 such as a boiler receives a significant heat input from, for example, an oil circuit 36 to vaporize the Siloxane MM working fluid with the vapor thereof passed through to the turbine 26 to provide motive power.
  • the relatively lower pressure working fluid vapor passes to the condenser/evaporator 32 and is condensed by way of a heat exchange relationship with the bottoming cycle 24 such that the condenser/evaporator 32 operates as a condenser in the topping cycle 22 as well as an evaporator in the bottoming cycle 24 .
  • the turbine 26 is a radial inflow turbine that expands the topping cycle working fluid vapor down to a lower pressure and generates power by the extraction of work from this expansion process.
  • the vapor is still superheated so that its heat potential is utilized in the condenser/evaporator 32 .
  • the condenser/evaporator 32 actually de-superheats the working fluid and ultimately condenses the working fluid back to liquid for communication through the pump 30 .
  • the condensed working fluid is then circulated to the evaporator 34 by the pump 30 to complete the topping cycle 22 .
  • the bottoming cycle 24 generally includes a power producing turbine 36 which is driven by the working fluid in the bottoming cycle and in turn drives a generator 38 that produces power.
  • a refrigerant pump 40 increases the pressure of the working fluid from a recuperator 40 .
  • the bottom cycle working fluid is in thermal communication with a cooling system such as a water circuit 42 through a water cooled condenser 44 .
  • the vapor entering and leaving turbine 36 is highly superheated.
  • the energy potential of the superheated vapor at the turbine exit is not wasted, but is fed into a recuperator 46 .
  • the recuperator 46 transfers heat from the low-pressure hot vapor from the turbine exit to the high pressure liquid at the pump exit.
  • the recuperator 46 uses this superheat to preheat the liquid working fluid downstream of the pump 40 . That is, if a cycle is driven to high turbine inlet superheat, then turbine outlet superheat will be high. The availability of this heat is thereby captured to maintain cycle efficiency as the recuperator 46 is an internal heat exchanger. When the low pressure side of the topping cycle 22 is de-superheated, it is essentially recuperated into the bottoming cycle 24 which is where high superheat is achieved. Matching of the working fluids and the pressures thereof facilitates this interaction.
  • the recuperator 46 is only in the bottoming cycle 24 . As the topping cycle 22 is not recuperated, its waste heat is captured by the condenser/evaporator 32 . Both cycles are highly superheated yet avoid heat-exchanger pinches to minimize the heat-transfer temperature difference and minimize process irreversibility
  • FIG. 2 shows a TS diagram for the bottoming cycle 24 .
  • the condenser/evaporator 32 receives nearly saturated liquid (a temperature that is close to boiling) from the recuperator 46 .
  • the condenser/evaporator 32 boils then heats the refrigerant from state 6 to 1.
  • the state 1 condition is highly superheated.
  • the exit state from the turbine 36 state 2, is also highly superheated.
  • the recuperator 46 uses this heat (state 2 to 3) to heat the high pressure working fluid (state 5 to 6). Sizing of the recuperator 46 affects state 6.
  • a smaller recuperator 46 results in less heat transferred and therefore a cooler more subcooled state at 6 which results in more heat transfer required from the condenser/evaporator 32 , and a larger percentage of that heat in the preheating and evaporating regimes.
  • FIG. 3 shows a TS diagram for the topping cycle 22 .
  • the exit state of the topping cycle turbine 26 is highly superheated, but a recuperator is not used. Instead, the low pressure working fluid vapor is de-superheated as the bottoming cycle high-pressure working fluid is superheated.
  • the choice of a heavy molecule such as Siloxane for the topping cycle 22 results in the highly angled saturation dome. As a result, the inlet state to turbine 26 is only slightly superheated.
  • FIG. 4 represents an idealized counter-flow heat exchanger.
  • the x-axis is normalized enthalpy change of each fluid, and the y-axis is temperature.
  • the x-axis is based on the First Law of Thermodynamics which can be written for a heat exchanger as:
  • ⁇ dot over (m) ⁇ A ( h A in ⁇ h A out ) ⁇ dot over (m) ⁇ B ( h B out ⁇ h B in )
  • m is the mass flow rate
  • h is the enthalpy of the fluid.
  • the warmer fluid (A) is shown to travel from right to left, and the colder fluid (B) to travel from left to right through the heat exchanger.
  • the above equation must be true. For example, the first 10% reduction in enthalpy of Fluid A must equal the last 10% increase of enthalpy of fluid B. If the fluids were simple fluids with constant specific heat, then each temperature profile would be a straight line. When the fluids are refrigerants, the temperature profiles have various non-linear shapes. When a fluid is saturated there is no change in temperature with change in enthalpy.
  • the change in temperature with enthalpy is generally different for a fluid as a liquid than as a vapor; therefore, the choice of fluid and operational temperatures affect the shape of these curves. Furthermore, the choice of other system components will affect their shape. Specifically the choice of and the size of the recuperator 46 in the proposed cycle affects the starting enthalpy (and therefore temperature) of stream B.
  • FIG. 4 shows how each temperature profile relates to the other at each physical location along the heat exchanger.
  • Fluid A In order for heat to flow from Fluid A to Fluid B, Fluid A must always be warmer than Fluid B. If A gets too close to B this is referred to as a temperature “pinch” condition. This is undesirable because a large heat exchange area is required to exchange the enthalpy in this region. In fact, the entire size of a heat exchanger may be defined by a “pinch” condition. Where the temperature difference is large, the thermodynamic cycle will be less efficient since more entropy is generated by heat exchange through larger temperature differences. An ideal arrangement is when the temperature difference throughout the heat exchanger remains relatively constant.
  • the condenser/evaporator 32 heat exchanger has two major regions. The first (on the left in FIG. 4 ) is saturated for both fluids and the temperature profiles are flat. This section covers about 40 percent of the total heat transfer in the disclosed non-limiting embodiment. The second (on the right in FIG. 4 ) is superheated and temperature increases with enthalpy. That is, a percent saturation for a fluid in the topping cycle 22 is maintained at 38 percent saturation compared to a 40 percent saturation for the working fluid in the bottoming cycle 24 .
  • the “knee” of fluid A must lie equal to or slightly to the left of the “knee” of fluid B in the normalized enthalpy plot. If the “knee” lies far to the left then the saturated section may have a good heat transfer difference (typically 5 to 15 F; 3 to 8 C), but the heat transfer difference of the vapor section will be too large. If the “knee” lies too far to the right then a “pinch” condition will be created between the two fluids. Practically the temperature difference will increase and the saturated temperature difference will be too high.
  • the effect of the recuperator 46 on the condenser/evaporator 32 in the proposed cycle is to change the inlet enthalpy, and therefore temperature, of the colder fluid, B.
  • the enthalpy of the inlet of B increases by recovering heat from the turbine exit. This results in a smaller percentage of the total heat transfer for Fluid B occurring to the left of the knee, shifts the knee of B to the left and results in a pinch condition.
  • the recuperator heat exchange is reduced or eliminated, this shifts knee of B to the right and therefore increases the temperature difference in the vapor section.
  • a percentage of total heat transfer from the working fluid in the topping cycle 22 that occurs during a saturated condensation is equal to or slightly less (within 10%) than a percentage of total heat transfer to the working fluid in the bottoming cycle 24 that occurs during a saturated evaporation.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
US13/334,994 2011-12-22 2011-12-22 Cascaded organic rankine cycle system Abandoned US20130160449A1 (en)

Priority Applications (5)

Application Number Priority Date Filing Date Title
US13/334,994 US20130160449A1 (en) 2011-12-22 2011-12-22 Cascaded organic rankine cycle system
SG2012075271A SG191468A1 (en) 2011-12-22 2012-10-09 Cascaded organic rankine cycle system
EP12195287.3A EP2607635B8 (de) 2011-12-22 2012-12-03 Kaskadiertes organisches Rankine-Kreislaufsystem
CA2798770A CA2798770C (en) 2011-12-22 2012-12-13 Cascaded organic rankine cycle system
CN201210561391.5A CN103174475B (zh) 2011-12-22 2012-12-21 级联有机兰金循环系统及其操作方法

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US13/334,994 US20130160449A1 (en) 2011-12-22 2011-12-22 Cascaded organic rankine cycle system

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EP (1) EP2607635B8 (de)
CN (1) CN103174475B (de)
CA (1) CA2798770C (de)
SG (1) SG191468A1 (de)

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CN105019959A (zh) * 2015-07-29 2015-11-04 昆明理工大学 一种复叠式有机朗肯循环系统
WO2017096280A3 (en) * 2015-12-03 2018-02-22 Eaton Corporation Oil free organic rankine cycle roots expander
EP3227533A4 (de) * 2014-10-31 2018-07-11 Subodh Verma System für hocheffizienten energieumwandlungszyklus durch recycling latenter verdunstungswärme
US20190093556A1 (en) * 2017-11-21 2019-03-28 Aestus Energy Storage, LLC Thermal storage system charging
US10577986B2 (en) 2016-04-22 2020-03-03 American Exchanger Services, Inc. Systems and methods for improving power plant efficiency
US10648701B2 (en) 2018-02-06 2020-05-12 Thermo Fisher Scientific (Asheville) Llc Refrigeration systems and methods using water-cooled condenser and additional water cooling
EP3536915A4 (de) * 2016-12-02 2020-06-24 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Wärmeenergierückgewinnungsvorrichtung und hochfahrbetriebsverfahren dafür
US10788203B2 (en) * 2015-09-08 2020-09-29 Atlas Copco Airpower, Naamloze Vennootschap ORC for transforming waste heat from a heat source into mechanical energy and compressor installation making use of such an ORC
US10895409B2 (en) 2017-11-21 2021-01-19 Aestus Energy Storage, LLC Thermal storage system charging
US11326479B2 (en) * 2018-11-13 2022-05-10 Lochterra, Inc. Systems and methods for the capture of heat energy, long-distance conveyance, storage, and distribution of the captured heat energy and power generated therefrom

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AU2015413548B2 (en) * 2014-10-31 2019-08-15 Subodh Verma A system for high efficiency energy conversion cycle by recycling latent heat of vaporization
EP3227533A4 (de) * 2014-10-31 2018-07-11 Subodh Verma System für hocheffizienten energieumwandlungszyklus durch recycling latenter verdunstungswärme
CN105019959A (zh) * 2015-07-29 2015-11-04 昆明理工大学 一种复叠式有机朗肯循环系统
US10788203B2 (en) * 2015-09-08 2020-09-29 Atlas Copco Airpower, Naamloze Vennootschap ORC for transforming waste heat from a heat source into mechanical energy and compressor installation making use of such an ORC
WO2017096280A3 (en) * 2015-12-03 2018-02-22 Eaton Corporation Oil free organic rankine cycle roots expander
US10577986B2 (en) 2016-04-22 2020-03-03 American Exchanger Services, Inc. Systems and methods for improving power plant efficiency
EP3536915A4 (de) * 2016-12-02 2020-06-24 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd.) Wärmeenergierückgewinnungsvorrichtung und hochfahrbetriebsverfahren dafür
WO2019104156A1 (en) * 2017-11-21 2019-05-31 Aestus Energy Storage, LLC Thermal storage system charging
US20190093556A1 (en) * 2017-11-21 2019-03-28 Aestus Energy Storage, LLC Thermal storage system charging
US10794277B2 (en) * 2017-11-21 2020-10-06 Aestus Energy Storage, LLC Thermal storage system charging
US10895409B2 (en) 2017-11-21 2021-01-19 Aestus Energy Storage, LLC Thermal storage system charging
US10648701B2 (en) 2018-02-06 2020-05-12 Thermo Fisher Scientific (Asheville) Llc Refrigeration systems and methods using water-cooled condenser and additional water cooling
US11326479B2 (en) * 2018-11-13 2022-05-10 Lochterra, Inc. Systems and methods for the capture of heat energy, long-distance conveyance, storage, and distribution of the captured heat energy and power generated therefrom
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EP2607635B1 (de) 2021-01-20
CN103174475A (zh) 2013-06-26
SG191468A1 (en) 2013-07-31
CA2798770C (en) 2015-11-17
EP2607635A2 (de) 2013-06-26
CN103174475B (zh) 2016-08-03
EP2607635A3 (de) 2017-03-29
CA2798770A1 (en) 2013-06-22
EP2607635B8 (de) 2021-03-24

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