US20150121866A1 - Rankine cycle mid-temperature recuperation - Google Patents
Rankine cycle mid-temperature recuperation Download PDFInfo
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- US20150121866A1 US20150121866A1 US14/397,523 US201214397523A US2015121866A1 US 20150121866 A1 US20150121866 A1 US 20150121866A1 US 201214397523 A US201214397523 A US 201214397523A US 2015121866 A1 US2015121866 A1 US 2015121866A1
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- Prior art keywords
- coolant
- boiler
- recuperator
- valve
- temperature
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- Abandoned
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- 239000002826 coolant Substances 0.000 claims abstract description 38
- 238000000034 method Methods 0.000 claims abstract description 8
- 238000005086 pumping Methods 0.000 claims abstract description 4
- 238000001816 cooling Methods 0.000 claims 1
- 239000003507 refrigerant Substances 0.000 description 5
- 239000007789 gas Substances 0.000 description 4
- 238000009428 plumbing Methods 0.000 description 4
- 239000012530 fluid Substances 0.000 description 3
- 230000005540 biological transmission Effects 0.000 description 2
- 238000010438 heat treatment Methods 0.000 description 2
- 239000007858 starting material Substances 0.000 description 2
- 239000002918 waste heat Substances 0.000 description 2
- 230000001133 acceleration Effects 0.000 description 1
- 230000003466 anti-cipated effect Effects 0.000 description 1
- 238000011156 evaluation Methods 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 238000004064 recycling Methods 0.000 description 1
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
- 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
- F01K23/06—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 combustion heat from one cycle heating the fluid in another cycle
- F01K23/10—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 combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
- F01K23/101—Regulating means specially adapted therefor
-
- 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
- F01K23/06—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 combustion heat from one cycle heating the fluid in another cycle
- F01K23/065—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 combustion heat from one cycle heating the fluid in another cycle the combustion taking place in an internal combustion piston engine, e.g. a diesel engine
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N5/00—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy
- F01N5/02—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy the devices using heat
Definitions
- a Rankine Cycle Waste Heat Recovery When a Rankine Cycle Waste Heat Recovery (RC-WHR) is applied to air systems (both clean air and EGR), it preferably delivers target air temperatures to be reached for engine emissions compliance. It also tries to achieve as high a cycle efficiency as possible for example to improve engine Brake Specific Fuel Consumption (BSFC). Additionally, recuperation is often desired to help increase the cycle efficiency, regardless, when very dry fluids with narrow P-h dome are used as coolant. However, with a recuperator for energy exchange between pump-out coolant and exhaust from expander in the conventional RC-WHR system, the amount of recuperation, which is limited by the coolant temperature flowing out of recuperator, is constrained by the target air temperature. This constraint limits the cycle efficiency and bsfc improvement from RC-WHR system.
- BSFC Brake Specific Fuel Consumption
- One or more embodiments provide a system and method for recuperation including a boiler wherein air and exhaust gas recirculation pass through the boiler and are cooled by thermal transfer with a coolant.
- the system includes an expander receiving coolant from the boiler, a recuperator receiving coolant from the expander, a condenser receiving coolant from the recuperator, a pump pumping coolant from the condenser to a low temperature portion of the boiler, and a valve, which allows coolant to pass directly from the boiler to the recuperator.
- FIG. 1 illustrates a conventional recuperation system.
- FIG. 2 illustrates the recuperation system of FIG. 1 in greater detail.
- FIG. 3 illustrates a modified recuperation system
- FIG. 4 illustrates the modified recuperation system of FIG. 3 in more detail.
- FIG. 5 illustrates the previous recuperator configuration operating at C100.
- FIG. 6 illustrates the new recuperator configuration operating at C100.
- FIG. 7 illustrates the new recuperator configuration operating at C100 and also at supercritical.
- FIG. 8 illustrates the prior recuperator configuration operating at B50.
- FIG. 9 illustrates the new recuperator configuration operating at B50.
- FIG. 10 illustrates the new recuperator configuration operating at B50 and also at supercritical.
- FIG. 1 illustrates a conventional recuperation system 100 .
- the recuperation system 100 includes an air plus exhaust gas recirculation (EGR) 110 , a boiler 120 , an expander 130 , a recuperator 140 , a condenser loop 145 , a condenser 150 , a pump 160 , and an intake manifold 170 .
- EGR air plus exhaust gas recirculation
- air plus EGR 110 is fed into the boiler 120 .
- An expander 130 is in fluid connection with the boiler and a recuperator 140 .
- Coolant flows from the boiler 120 to the expander 130 and then to the recuperator 140 .
- Some coolant passes from the recuperator 140 into the condenser loop 145 where the coolant then passes through the condenser 150 and is pumped by pump 160 back to the recuperator 140 .
- coolant passes from the recuperator 140 back to the boiler 120 .
- the coolant in the boiler 120 acts to reduce the temperature of the air plus EGR 110 until the desired temperature at the intake manifold is achieved.
- FIG. 2 illustrates the recuperation system 100 of FIG. 1 in greater detail.
- FIG. 2 includes the boiler 120 , the expander 130 , the recuperator 140 , the air cooled condenser 150 and the pump 160 of FIG. 1 and additionally includes a transmission 180 , an integrated starter generator (ISG) 182 , an Inverter and Control 184 , a turbogenerator 186 , a high temperature radiator 188 , an A/C condenser 190 , and an accumulator 192 .
- ISG integrated starter generator
- FIG. 3 illustrates a modified recuperation system 200 .
- the modified recuperation system 200 includes an air plus exhaust gas recirculation (EGR) 210 , a boiler 220 , an expander 230 , a recuperator 240 , a condenser loop 245 , a condenser 250 , a pump 260 , an intake manifold 270 , a multi-position three-way valve 265 , and an intake manifold 270 .
- the modified recuperation system 200 of FIG. 3 provides the ability to apply Rankine Cycle-Waste Heat Recycling (RC-WHR) systems to the air system (both clean air and EGR) and develop a match between dry fluids and such a RC system is a new and developing area.
- RC-WHR Rankine Cycle-Waste Heat Recycling
- the coolant is first directed to the low temperature section of heat exchanger (boiler) 220 . After heated up to a certain degree, the refrigerant is routed to recuperator 240 for recuperation, and then introduced back to boiler 220 for further heating.
- the target temperature is not a constraint to recuperation any more.
- the target temperature may be easily assured. For example, the temperature in the intake manifold 270 may be measured using a temperature sensor 268 .
- Data from the temperature sensor 260 may be passed to a valve control 267 to determine the settings for the valve 265 , that is whether the valve should be opened more, closed more, or remain in the same setting so as to deliver the desired temperature at the intake manifold 270 .
- the target intake manifold temperature and the better BSFC improvement may both be achieved in such a system.
- the target air temperature (fresh air+EGR) at the intake manifold may now be maintained more accurately and consistently under all operating conditions.
- FIG. 4 illustrates the modified recuperation system of FIG. 2 in more detail.
- the modified recuperation system includes the boiler 220 , the expander 230 , the recuperator 240 , the condenser 250 , the pump 270 of FIG. 3 and additionally includes a transmission 280 , an integrated starter generator (ISG) 282 , an Inverter and Control 284 , a turbogenerator 286 , a high temperature radiator 288 , an A/C condenser 290 , and an accumulator 292 .
- the new heat exchanger may replace the current air system coolers (EGR, Charge Air Cooler (CAC), and/or Inter-stage cooler (ISC)
- coolants having a dry, narrow and much skewed P-h dome lead to large portion of energy contained in dry exhaust from the expander. This constitutes a great potential for recuperation, even with little superheat.
- the refrigerant from pump goes to the low temperature portion of boiler to ensure the IMT temperature is at target. After heating up to a certain degree, the refrigerant is directed to the recuperator, where a larger portion of exhaust heat can be recuperated. For example, up to 30% of boiler total heat transfer may take place in the low temperature portion of the boiler in the analysis below.
- comparison of the new plumbing design (of FIG. 3 ) to the conventional design (of FIG. 1 ) shows that the new plumbing design results in a better cycle thermal efficiency (by approximately 20%) and BSCF improvement (by approximately 1%), compared to the original design at the same conditions. This is illustrated in FIGS. 5-10 , which illustrate the conventional system of FIG. 1 and the modified system of FIG.
- a first condition referenced as C100
- B50 describes an engine operating point approximating that of an engine cruising on a highway
- FIG. 5 illustrates the previous recuperator configuration 500 operating at C100.
- FIG. 5 also shows the intake air and EGR 510 , boiler 520 , expander 530 , recuperator 540 , condenser 550 , and pump 560 .
- the power recovered from the expander is 21.75 kW.
- the ⁇ thermal (thermal efficiency) is 9.85%
- the Pinch is 10.0 C
- the BSFC increase is 5.26%.
- FIG. 6 illustrates the new recuperator configuration 600 operating at C100.
- FIG. 6 also shows the intake air and EGR 610 , boiler 620 , expander 630 , recuperator 640 , condenser 650 , and pump 660 .
- the power recovered from the expander is now 27.36 kW—up from 21.75 kW in FIG. 5 —an increase of more than 6 kW.
- the ⁇ thermal is 12.39%
- the Pinch is 10.5 C
- the BSFC increase is 6.53%.
- FIG. 7 illustrates the new recuperator configuration 700 operating at C100 and also at supercritical.
- FIG. 7 also shows the intake air and EGR 710 , boiler 720 , expander 730 , recuperator 740 , condenser 750 , and pump 760 .
- the power recovered from the expander is now 28.8 kW—up from 21.75 kW in FIG. 5 —an increase of more than 7 kW.
- the ⁇ thermal is 12.72%
- the Pinch is 10.6 C
- the BSFC increase is 6.69%.
- FIG. 8 illustrates the prior recuperator configuration 800 operating at B50.
- FIG. 8 also shows the intake air and EGR 810 , boiler 820 , expander 830 , recuperator 840 , condenser 850 , and pump 860 .
- the power recovered from the expander is 10.84 kW.
- the ⁇ thermal is 9.79%
- the Pinch is 10.0 C
- the BSFC increase is 5.46%.
- FIG. 9 illustrates the new recuperator configuration 900 operating at B50.
- FIG. 9 also shows the intake air and EGR 910 , boiler 920 , expander 930 , recuperator 940 , condenser 950 , and pump 960 .
- the power recovered from the expander is now 12.88 kW—up from 10.84 kW in FIG. 8 —an increase of more than 2 kW.
- the ⁇ thermal is 11.66%
- the Pinch is 10.5 C
- the BSFC increase is 6.44%.
- FIG. 10 illustrates the new recuperator configuration 1000 operating at B50 and also at supercritical.
- FIG. 10 also shows the intake air and EGR 1010 , boiler 1020 , expander 1030 , recuperator 1040 , condenser 1050 , and pump 1060 .
- the power recovered from the expander is now 14.2 kW—up from 10.84 kW in FIG. 8 —an increase of about 3.5 kW.
- the ⁇ thermal is 12.49%
- the Pinch is 10.6 C
- the BSFC increase is 6.87%.
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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)
Abstract
Description
- When a Rankine Cycle Waste Heat Recovery (RC-WHR) is applied to air systems (both clean air and EGR), it preferably delivers target air temperatures to be reached for engine emissions compliance. It also tries to achieve as high a cycle efficiency as possible for example to improve engine Brake Specific Fuel Consumption (BSFC). Additionally, recuperation is often desired to help increase the cycle efficiency, regardless, when very dry fluids with narrow P-h dome are used as coolant. However, with a recuperator for energy exchange between pump-out coolant and exhaust from expander in the conventional RC-WHR system, the amount of recuperation, which is limited by the coolant temperature flowing out of recuperator, is constrained by the target air temperature. This constraint limits the cycle efficiency and bsfc improvement from RC-WHR system.
- One or more embodiments provide a system and method for recuperation including a boiler wherein air and exhaust gas recirculation pass through the boiler and are cooled by thermal transfer with a coolant. The system includes an expander receiving coolant from the boiler, a recuperator receiving coolant from the expander, a condenser receiving coolant from the recuperator, a pump pumping coolant from the condenser to a low temperature portion of the boiler, and a valve, which allows coolant to pass directly from the boiler to the recuperator.
-
FIG. 1 illustrates a conventional recuperation system. -
FIG. 2 illustrates the recuperation system ofFIG. 1 in greater detail. -
FIG. 3 illustrates a modified recuperation system. -
FIG. 4 illustrates the modified recuperation system ofFIG. 3 in more detail. -
FIG. 5 illustrates the previous recuperator configuration operating at C100. -
FIG. 6 illustrates the new recuperator configuration operating at C100. -
FIG. 7 illustrates the new recuperator configuration operating at C100 and also at supercritical. -
FIG. 8 illustrates the prior recuperator configuration operating at B50. -
FIG. 9 illustrates the new recuperator configuration operating at B50. -
FIG. 10 illustrates the new recuperator configuration operating at B50 and also at supercritical. -
FIG. 1 illustrates aconventional recuperation system 100. Therecuperation system 100 includes an air plus exhaust gas recirculation (EGR) 110, aboiler 120, anexpander 130, arecuperator 140, acondenser loop 145, acondenser 150, apump 160, and anintake manifold 170. - In operation, air plus EGR 110 is fed into the
boiler 120. Anexpander 130 is in fluid connection with the boiler and arecuperator 140. Coolant flows from theboiler 120 to theexpander 130 and then to therecuperator 140. Some coolant passes from therecuperator 140 into thecondenser loop 145 where the coolant then passes through thecondenser 150 and is pumped bypump 160 back to therecuperator 140. Finally, coolant passes from therecuperator 140 back to theboiler 120. The coolant in theboiler 120 acts to reduce the temperature of the air plus EGR 110 until the desired temperature at the intake manifold is achieved. -
FIG. 2 illustrates therecuperation system 100 ofFIG. 1 in greater detail.FIG. 2 includes theboiler 120, theexpander 130, therecuperator 140, the air cooledcondenser 150 and thepump 160 ofFIG. 1 and additionally includes atransmission 180, an integrated starter generator (ISG) 182, an Inverter andControl 184, aturbogenerator 186, ahigh temperature radiator 188, an A/C condenser 190, and anaccumulator 192. -
FIG. 3 illustrates amodified recuperation system 200. The modifiedrecuperation system 200 includes an air plus exhaust gas recirculation (EGR) 210, aboiler 220, anexpander 230, arecuperator 240, a condenser loop 245, acondenser 250, apump 260, anintake manifold 270, a multi-position three-way valve 265, and anintake manifold 270. The modifiedrecuperation system 200 ofFIG. 3 provides the ability to apply Rankine Cycle-Waste Heat Recycling (RC-WHR) systems to the air system (both clean air and EGR) and develop a match between dry fluids and such a RC system is a new and developing area. - More specifically, instead of plumbing or piping the coolant (or refrigerant) from the
pump 260 directly to therecuperater 240, the coolant is first directed to the low temperature section of heat exchanger (boiler) 220. After heated up to a certain degree, the refrigerant is routed torecuperator 240 for recuperation, and then introduced back toboiler 220 for further heating. By piping the coolant in this way, the target temperature is not a constraint to recuperation any more. By adding a multi-position 3-way valve 265, the target temperature may be easily assured. For example, the temperature in theintake manifold 270 may be measured using atemperature sensor 268. Data from thetemperature sensor 260 may be passed to avalve control 267 to determine the settings for thevalve 265, that is whether the valve should be opened more, closed more, or remain in the same setting so as to deliver the desired temperature at theintake manifold 270. - Consequently, by carefully designing the two sections of the
boiler 120, a larger amount of energy may be recuperated, thus increasing the cycle efficiency and providing a BSFC improvement. Additionally, the target intake manifold temperature and the better BSFC improvement may both be achieved in such a system. Stated another way, the target air temperature (fresh air+EGR) at the intake manifold may now be maintained more accurately and consistently under all operating conditions. -
FIG. 4 illustrates the modified recuperation system ofFIG. 2 in more detail. The modified recuperation system includes theboiler 220, theexpander 230, therecuperator 240, thecondenser 250, thepump 270 ofFIG. 3 and additionally includes atransmission 280, an integrated starter generator (ISG) 282, an Inverter andControl 284, aturbogenerator 286, ahigh temperature radiator 288, an A/C condenser 290, and anaccumulator 292. For some embodiments, the new heat exchanger (boiler) may replace the current air system coolers (EGR, Charge Air Cooler (CAC), and/or Inter-stage cooler (ISC) - With regard to coolants, coolants having a dry, narrow and much skewed P-h dome lead to large portion of energy contained in dry exhaust from the expander. This constitutes a great potential for recuperation, even with little superheat.
- In the prior plumbing setup shown in
FIG. 1 , refrigerant from the pump first recuperates the exhaust energy from the expander and then goes to the boiler. The actual amount of recuperation is constrained by intake manifold temperature, IMT, resulting in still-high-temperature exhaust energy unused and more burden on the condenser, which limits overall BSFC improvement up to 5.5%. - In the new setup shown in
FIG. 3 , the refrigerant from pump goes to the low temperature portion of boiler to ensure the IMT temperature is at target. After heating up to a certain degree, the refrigerant is directed to the recuperator, where a larger portion of exhaust heat can be recuperated. For example, up to 30% of boiler total heat transfer may take place in the low temperature portion of the boiler in the analysis below. Additionally, comparison of the new plumbing design (ofFIG. 3 ) to the conventional design (ofFIG. 1 ) shows that the new plumbing design results in a better cycle thermal efficiency (by approximately 20%) and BSCF improvement (by approximately 1%), compared to the original design at the same conditions. This is illustrated inFIGS. 5-10 , which illustrate the conventional system ofFIG. 1 and the modified system ofFIG. 3 at different operating conditions. In particular, in the Figures and the following description, a first condition, referenced as C100, describes an engine operating point approximating that of undergoing heavy hauling and/or acceleration. Likewise, a second operating condition, referenced as B50, describes an engine operating point approximating that of an engine cruising on a highway - Additionally, at supercritical conditions, where the coolant's temperature and pressure exceed a boundary point and take on properties between those of a liquid and a gas, additional changes occur. More specifically, supercritical conditions provide higher expansion ratio, and as anticipated, cycle efficiency is improved, but at much more moderate margin. The selection of maximum system pressure also requires evaluation of system weight.
-
FIG. 5 illustrates theprevious recuperator configuration 500 operating at C100.FIG. 5 also shows the intake air and EGR 510,boiler 520, expander 530,recuperator 540,condenser 550, andpump 560. As shown inFIG. 5 , the power recovered from the expander is 21.75 kW. Additionally, the ηthermal (thermal efficiency) is 9.85%, the Pinch is 10.0 C, and the BSFC increase is 5.26%. -
FIG. 6 illustrates thenew recuperator configuration 600 operating at C100.FIG. 6 also shows the intake air andEGR 610,boiler 620,expander 630,recuperator 640,condenser 650, and pump 660. However, as shown inFIG. 6 , the power recovered from the expander is now 27.36 kW—up from 21.75 kW in FIG. 5—an increase of more than 6 kW. Additionally, the ηthermal is 12.39%, the Pinch is 10.5 C, and the BSFC increase is 6.53%. -
FIG. 7 illustrates thenew recuperator configuration 700 operating at C100 and also at supercritical.FIG. 7 also shows the intake air andEGR 710,boiler 720,expander 730,recuperator 740,condenser 750, and pump 760. However, as shown inFIG. 7 , the power recovered from the expander is now 28.8 kW—up from 21.75 kW in FIG. 5—an increase of more than 7 kW. Additionally, the ηthermal is 12.72%, the Pinch is 10.6 C, and the BSFC increase is 6.69%. -
FIG. 8 illustrates theprior recuperator configuration 800 operating at B50.FIG. 8 also shows the intake air andEGR 810,boiler 820,expander 830,recuperator 840,condenser 850, and pump 860. As shown inFIG. 8 , the power recovered from the expander is 10.84 kW. Additionally, the ηthermal is 9.79%, the Pinch is 10.0 C, and the BSFC increase is 5.46%. -
FIG. 9 illustrates thenew recuperator configuration 900 operating at B50.FIG. 9 also shows the intake air andEGR 910,boiler 920,expander 930,recuperator 940,condenser 950, and pump 960. However, as shown inFIG. 9 , the power recovered from the expander is now 12.88 kW—up from 10.84 kW in FIG. 8—an increase of more than 2 kW. Additionally, the ηthermal is 11.66%, the Pinch is 10.5 C, and the BSFC increase is 6.44%. -
FIG. 10 illustrates thenew recuperator configuration 1000 operating at B50 and also at supercritical.FIG. 10 also shows the intake air andEGR 1010,boiler 1020,expander 1030,recuperator 1040,condenser 1050, andpump 1060. However, as shown inFIG. 10 , the power recovered from the expander is now 14.2 kW—up from 10.84 kW in FIG. 8—an increase of about 3.5 kW. Additionally, the ηthermal is 12.49%, the Pinch is 10.6 C, and the BSFC increase is 6.87%.
Claims (12)
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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PCT/US2012/036403 WO2013165431A1 (en) | 2012-05-03 | 2012-05-03 | Rankine cycle mid-temperature recuperation |
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US20150121866A1 true US20150121866A1 (en) | 2015-05-07 |
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ID=49514684
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US14/397,523 Abandoned US20150121866A1 (en) | 2012-05-03 | 2012-05-03 | Rankine cycle mid-temperature recuperation |
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WO (1) | WO2013165431A1 (en) |
Cited By (2)
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WO2017111886A1 (en) * | 2015-12-21 | 2017-06-29 | Cummins Inc. | Integrated control system for engine waste heat recovery using an organic rankine cycle |
US10570784B2 (en) | 2017-09-22 | 2020-02-25 | Tenneco Gmbh | Rankine power system for use with exhaust gas aftertreatment system |
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US11092041B2 (en) | 2017-09-22 | 2021-08-17 | Tenneco Gmbh | Condenser assembly and control method for use with Rankine power system |
US11118482B2 (en) | 2017-09-22 | 2021-09-14 | Tenneco Gmbh | Rankine power system for use with exhaust gas aftertreatment system |
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