CN105209724A - Volumetric energy recovery system with three stage expansion - Google Patents
Volumetric energy recovery system with three stage expansion Download PDFInfo
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- CN105209724A CN105209724A CN201480017926.XA CN201480017926A CN105209724A CN 105209724 A CN105209724 A CN 105209724A CN 201480017926 A CN201480017926 A CN 201480017926A CN 105209724 A CN105209724 A CN 105209724A
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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
- F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
- F01K7/16—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type
- F01K7/22—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type the turbines having inter-stage steam heating
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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
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D13/00—Combinations of two or more machines or engines
- F01D13/003—Combinations of two or more machines or engines with at least two independent shafts, i.e. cross-compound
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
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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
- F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
- F01K23/12—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engines being mechanically coupled
- F01K23/16—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engines being mechanically coupled all the engines being turbines
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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
- F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
- F01K7/02—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of multiple-expansion type
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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
- F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
- F01K7/16—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine 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
- F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
- F01K7/34—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of extraction or non-condensing type; Use of steam for feed-water heating
- F01K7/36—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of extraction or non-condensing type; Use of steam for feed-water heating the engines being of positive-displacement type
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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
- F01K9/00—Plants characterised by condensers arranged or modified to co-operate with the engines
- F01K9/02—Arrangements or modifications of condensate or air pumps
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Hydraulic Motors (AREA)
Abstract
A method for generating mechanical work via a closed-loop Rankine cycle includes heating a working fluid to at least a partial vapor state, generating useful work at a first expansion stage by expanding the working fluid as the working fluid passes through the first expansion stage, generating useful work at a second expansion stage by expanding the working fluid as the working fluid passes through the second expansion stage, generating useful work at a third expansion stage by expanding the working fluid as the working fluid passes through the third expansion stage, and condensing the working fluid to a liquid state.
Description
Related application
1. the application submitted to as pct international patent application on January 28th, 2014, require the U.S. Patent Application Serial Number 61/757 submitted on January 28th, 2013, the preference of 533, require the U.S. Patent Application Serial Number 61/810 submitted on April 10th, 2013, the preference of 579, and require the preference of the U.S. Patent Application Serial Number 61/816,143 submitted on April 25th, 2013.The full content of each application 61/757,533,61/810,579 and 61/816,143 is incorporated in this by reference.
Governmental approval right
2. the contract number No.DE-EE0005650 that the present invention authorizes according to the National Energy Technology laboratory that energy efficiency and the renewable energy sources office by U.S. Department of Energy provides funds completes under government-funded.Government has certain right to the present invention.
Technical field
3. the present invention relates to a kind of displacement fluid expander for producing power in Rankine cycle (Rankinecycle).
Background technique
4. Rankine cycle is a kind of is the power generation cycle of mechanical work by thermal energy.Rankine cycle is generally used in thermo-motor, and completes above-mentioned conversion by making operation material forward lower temperature state to from higher temperature state.Classical Rankine cycle is the elementary heat mechanical process of the operation based on steamer.
5., in Rankine cycle, heat " source " produces heat energy, and this heat energy makes operation material reach higher temperature state.Operation material is acting in " working body " of motor, heat is delivered to colder " radiator (sink) " until operation material reaches lower state of temperature simultaneously.In the process, by utilizing the characteristic of operation material, some heat energy are converted into merit.Heat is fed into the operation material in closed-loop path outside, and wherein, described operation material is the fluid with non-zero thermal capacitance, and it can be gas or liquid, such as water.The efficiency of Rankine cycle usually limit by working fluid.
6. Rankine cycle adopts independent subtense angle usually, as heat exchanger and the expander formula turbo machine of condenser, fluid pump, such as ebullator.The working fluid as liquid instead of gas that described pump usually receives from condenser for pressurizeing.Usually, all energy lose in pumping work fluid is by the process of complete cycle, and most of vaporization energy of the working fluid in ebullator is also like this.Therefore energy loses in the circulating cycle, main because the condensation that can occur in the turbine is limited in about 10% to make the erosion minimization of turbine blade, and this circulation refusal vaporization energy passes through condenser.On the other hand, with the fluid-phase ratio compressed in compressor as gas, pumping needs the relatively little share of the energy carried needed for fluid by this circulation as the working fluid of liquid.
7. a modification of the Rankine cycle of classics is organic Rankine bottoming cycle (ORC), and its name is owing to using organic polymer mass flow, and have than water-vapour change low temperature mutually under liquid-vapour phase of occurring become or boiling point.Like this, substituting as the water and steam in the Rankine cycle of classics, the working fluid in ORC can be solvent, such as pentane (n-pentane) or toluene.ORC working fluid allows from the Rankine cycle heat recovery in lower temperature source, as from biomass combustion, industrial waste heat, underground heat, solar pond etc.Then low-temperature heat quantity can be converted into useful work, and this useful work can be converted into electric power then.
Summary of the invention
8. generally speaking, the present invention relates to a kind of positive displacement energy-recuperation system with three grades of expansion systems.In a kind of feasible configuration and by non-limiting example, the present invention relates to a kind of via closed loop Rankine cycle to produce the method for mechanical work, the method comprises: working fluid is at least heated to partial vapor state; By working fluid from the first expansion stages by time make expansion of working fluid and the first expansion stages, produce useful work; By working fluid from the second expansion stages by time make expansion of working fluid produce useful work the second expansion stages; By working fluid from the 3rd expansion stages by time make expansion of working fluid produce useful work the 3rd expansion stages; And make working fluid be condensed to liquid condition.9. another aspect of the present invention relates to a kind of being used for via closed loop Rankine cycle to produce the system of mechanical work, and this system comprises: power equipment, and this power equipment produces hot-fluid and has the heat outlet that heat supply stream leaves; Be configured to spread from hot-fluid to working fluid hot heat-exchanger rig; Be configured to receive the first displacement fluid expansion stages from the working fluid stream of First Heat Exchanger; Be configured to receive the second displacement fluid expansion stages from the working fluid stream of the first displacement fluid expansion stages; And be configured to receive the 3rd displacement fluid expansion stages from the working fluid stream of the second displacement fluid expansion stages.First, second, and third displacement fluid expansion stages is configured to from the raw mechanical work of working fluid miscarriage.
Accompanying drawing explanation
10. Fig. 1 is the schematic diagram of the first example system using the Rankine cycle of three grades of expansion systems according to the employing of principle of the present invention.
11. Fig. 2 are the schematic diagram of the second example system using the Rankine cycle of three grades of expansion systems according to the employing of principle of the present invention.
12. Fig. 3 are the schematic diagram of the 3rd example system using the Rankine cycle of three grades of expansion systems according to the employing of principle of the present invention.
13. Fig. 4 are the flow charts of the illustrative methods had in the Rankine cycle of three grades of expansion systems.14. Fig. 5 are the flow charts of another illustrative methods had in the Rankine cycle of three grades of expansion systems.15. Fig. 6 are the flow charts of the another illustrative methods had in the Rankine cycle of three grades of expansion systems.16. Fig. 7 are side perspective of an example of the displacement fluid expander of the feature of the example of the aspect had as principle according to the present invention.
17. Fig. 8 are cross section side perspective of the displacement fluid expander shown in Fig. 7.
18. Fig. 9 are side cross-sectional view of an example of the displacement fluid expander of the feature of the example of the aspect had as principle according to the present invention.
19. Figure 10 are schematic perspective top view of the displacement fluid expander shown in Fig. 9.
20. Figure 11 show the schematic diagram of the geometric parameter of the rotor of the displacement fluid expander shown in Fig. 7 and 9.
21. Figure 12 show the schematic diagram of the rotor of the displacement fluid expander shown in Fig. 7 and 9.
22. Figure 13 are charts that the Rankine cycle that the system shown in Fig. 1-6 adopts is shown.
Embodiment
23. describe various embodiment in detail with reference to accompanying drawing, and wherein in whole multiple view, same reference character represents same part and assembly.The discussion of various embodiment is not limit the scope of the invention.In addition, any example described in this manual not intended to be is restrictive, but a lot of of claims are only described may some mode of executions in mode of executions.
24. with reference to accompanying drawings that show such system: the used heat in the always ultromotivity source (being also called as power plant in literary composition) of multiple displacement fluid expansion stages 20 wherein with the wrong rotor of double cross extracts otherwise the energy that will be wasted.As described below, rotor can be configured to straight or to reverse.Displacement fluid expansion stages 20 also can be called as expander, expansion gear or positive displacement energy recycle device in the text.Energy-recuperation system is formed by being connected with the carry-out part of the displacement fluid expansion stages directly or indirectly energy being transmitted back to power plant by component.
25.
there is the positive displacement energy-recuperation system of three grades of expansion systems
26. Fig. 1 are the schematic diagram of the system 100 using the Rankine cycle of three grades of expansion systems according to the employing of principle of the present invention.In this example, system 100 adopts working fluid 12 as the operation material for closed loop cycle when utilizing Rankine cycle to produce mechanical work.Working fluid 12 can belong to any type of applicable Rankine cycle.In some instances, working fluid is ethanol, pentane or toluene.In the literature, working fluid 12 is expressed as different reference character, such as 13,14,17,22,23,16,27,28,30 and 32, to represent the not homophase of fluid 12, temperature and/or pressure.
27. in some instances, and system 100 comprises: motor 52; Multiple heat exchanger 18-1,18-2,18-3 and 18-4 (being collectively expressed as 18); Three grades of expansion systems, it has multiple expansion stages 20-1,20-2 and 20-3 (being collectively expressed as 20); Condenser 25; With fluid pump 16.
28. motors 52 can be rely on chemical fuel operate as the burning of bavin Water Oil Or Gas and produce the explosive motor of large calorimetric and exhaust.In some instances, motor 52 can comprise pressurized machine or turbosupercharger 102 and forces super charge to use.
More than 29. heat exchanger 18 is configured to conduct heat to/from through working fluid 12 wherein.
30. expansion stages 20 are configured to receive working fluid 12 and produce mechanical work.Be in operation, along with working fluid 12 passes through from expansion stages 20, the temperature and pressure of fluid 12 declines.Generally speaking, the pressure that expansion stages 20 depends on fluid 12 rotates to make output shaft, forms mechanical energy thus.Mechanical energy can be used in many ways or be stored.Such as, the torque formed by expansion stages 20 can be used by motor 52.Each expansion stages 20 can make extracted energy via output shaft 38 return engine 52 (Fig. 3-6) of device 20.In other example, mechanical energy can be accumulated in load reservoir device to discharge as required from now on.The oil hydraulic pump that mechanical energy also can be used to the generator relevant to system 100 or be used by motor 52.Therefore, displacement fluid expansion stages 20 operates the total efficiency improving motor 52, diligent to be formed, and makes fluid 12 recirculation.Hereinafter with reference Fig. 3-6 discusses the example of expansion stages 20 in more detail.
31. condensers 25 operate to make it be condensed to liquid state from its gaseous state by making working fluid 12 cool.32. fluid pumps 16 are configured to working fluid 12 to deliver to high pressure from low pressure pump, and maintenance work fluid 12 is in its liquid state simultaneously.
33. with reference to Fig. 1, and on-stream, motor 52 is through turbine 102 admission of air.Turbine 102 receives and is in air 103 under temperature T1 and air 103 is cooled to the air 106 be under the temperature T2 lower than temperature T1 by charge air cooler 104.Then the air 106 be under temperature T2 is transported to motor 52 and is used by it, and after this motor 52 discharges the exhaust 108 be under the temperature T3 higher than temperature T2.
34. exhausts 108 be under temperature T3 enter First Heat Exchanger 18-1.Heat exchanger 18-1 adopt flow wherein be in fluid 14 under temperature T9 as cooling fluid.Temperature T9 is lower than temperature T3.As discussed below, fluid 14 is discharged from the first expansion stages 20-1.First Heat Exchanger 18-1 makes fluid 14 cycle through its coil pipe, and when fluid 14 flows through coil pipe, coolant exhaust 108 also adds hot fluid 14 to produce the fluid 13 be under the temperature T11 higher than temperature T9 simultaneously thus.Then the fluid 13 through heating be under temperature T11 passes through from the second expansion stages 20-2.
35. second expansion stages 20-2 receptions are in fluid 13 fluid 17 of source under the temperature T12 lower than T11 side by side under temperature T11.In addition, fluid 17 has the pressure lower than fluid 12.While the temperature and pressure reducing fluid 13 is fluid 17, the second expansion stages 20-2 produces the mechanical work that can be used in every way as mentioned above or store.
36. fluids 17 with the temperature and pressure lower than fluid 13 flow through the 3rd expansion stages 20-3 immediately, the 3rd expansion stages when its discharges the fluid 21 be under the temperature T4 lower than temperature T12 again for the formation of mechanical energy.In addition, fluid 21 has the pressure lower than fluid 17.Because fluid 17 has the temperature and pressure lower than fluid 13 when it enters the 3rd expansion stages 20-3, so the 3rd expansion stages 20-3 can not produce the so much mechanical energy of the second expansion stages 20-2.Therefore, the fluid 21 leaving the 3rd expansion stages 20-3 has the temperature and pressure lower than fluid 17 and 13.In some instances, the fluid 21 leaving the 3rd expansion stages 20-3 has the mixed phase fluid of the mixture comprising gas and liquid.Then 37. fluids 21 be under temperature T4 passed through from the second heat exchanger 18-2 before inflow condenser 25, and this second heat exchanger is commonly called recuperator.Recuperator 18-2 is arranged between the 3rd expansion stages 20-3 and condenser 25, to recycle the used heat of the fluid 21 since the 3rd expansion stages 20-3 release.The fluid 23 leaving recuperator 18-2 has the temperature T10 lower than temperature T4.
38. fluids 23 fluid 23 be then sent to for the mixture by can be gas and liquid is in some instances converted into the condenser 25 of the saturated liquids 31 be under temperature T5.As shown in the Rankine cycle of Fig. 7, temperature T5 keeps substantially identical at condenser 25 place, and therefore temperature T5 and T10 is substantially identical.
39. fluids 31 be under temperature T5 deliver to high pressure by pump 16 from low pressure pump.In the process, the temperature T5 of fluid 31 raises, as shown in the Rankine cycle of Fig. 7.Therefore, the fluid 27 of discharging from pump 16 has the temperature T13 higher than the temperature T5 of fluid 31, and flows into recuperator 18-2.The fluid 27 that 40. recuperator 18-2 utilizations are under temperature T13 absorbs heat from fluid 21, and described fluid 21 discharges from the 3rd expansion stages 20-3.Therefore, the heat trnasfer from the fluid 21 be under temperature T4 to the fluid 27 be under temperature T13, is produced the fluid 33 be under the temperature T6 higher than temperature T13 by recuperator 18-2 thus.Fluid 33 flows to the 3rd heat exchanger 18-3.
The heat of the exhaust 108 that 41. the 3rd heat exchanger 18-3 discharge since First Heat Exchanger 18-1 is in the future delivered to fluid 33, produces the fluid 35 be under the temperature T7 higher than T6 thus.After this fluid 35 flows to the 4th heat exchanger 18-4.
42. the 4th heat exchanger 18-4 by from motor 52, the heat trnasfer being in the exhaust 108 under temperature T3 that flows through the 4th heat exchanger 18-4 is to the fluid 35 be under temperature T7.As a result, the 4th heat exchanger 18-4 produces the fluid 36 be under the temperature T8 higher than T7.Exhaust 108 is simultaneously cooled when it flows through the 4th heat exchanger 18-4 to the temperature lower than T3 and is released to air.
43. fluids 36 be under temperature T8 are in the fluid 14 of the temperature T9 lower than T8 by discharge and the first expansion stages 20-1 of generation mechanical work described above receives.Fluid 14 has the pressure lower than fluid 36.The fluid 14 leaving the first expansion stages 20-1 under temperature T9 flows directly to First Heat Exchanger 18-1, and at this, it is directly heated by the exhaust 108 supplied from motor 52 again.Then whole process repeats in circulation as above.
44. as mentioned above, and the second heat exchanger (being also referred to as recuperator) 18-2, the 3rd heat exchanger 18-3 and the 4th heat exchanger 18-4 are connected in series.In some instances, second heat exchanger 18-2, the 3rd heat exchanger 18-3 and the 4th heat exchanger 18-4 are replaced by one or two heat exchanger apparatus, and described heat exchanger apparatus is to work with the second heat exchanger 18-2, mode that the 3rd heat exchanger 18-3 is identical with the combination of the 4th heat exchanger 18-4.
45. Fig. 2 are the schematic diagram of the second example system 100 using the Rankine cycle of three grades of expansion systems according to the employing of principle of the present invention.Because many concepts are similar with the first example shown in feature to Fig. 1, therefore being described in this and being incorporated to the second example by reference the first example.When showing same or similar feature or element, identical reference character will be used as far as possible.Below for the difference that the description of the second example will be mainly limited between the first example and the second example.
46. in this example, and system 100 removes First Heat Exchanger 18-1.In a first example, be in fluid 14 under temperature T9 discharge from the first expansion stages 20-1 and advance into First Heat Exchanger 18-1 at inflow second expansion stages 20-2.Comparatively speaking, in this example, the fluid 14 be in temperature T9 of discharging from the first expansion stages 20-1 is delivered directly to the second expansion stages 20-2.In addition, in a first example, the exhaust 108 be in temperature T3 supplied from motor 52 is successively passed through from First Heat Exchanger 18-1 and the 3rd heat exchanger 18-3.But in this example, the exhaust 108 be under temperature T3 directly flows to the 3rd heat exchanger 18-3 from motor 52.
47. Fig. 3 are the schematic diagram of the 3rd example system 100 using the Rankine cycle of three grades of expansion systems according to the employing of principle of the present invention.Because many concepts are similar with the second example shown in feature to Fig. 2, so being described in this and being incorporated to the 3rd example by reference for the second example.When showing same or similar feature or element, identical reference character will be used as far as possible.Below for the difference that the description of the 3rd example will be mainly limited between the second example and the 3rd example.
48. in this example, and recuperator 18-2 is directly connected with the 3rd heat exchanger 18-3 and the 4th heat exchanger 18-4, and the 3rd heat exchanger 18-3 and the 4th heat exchanger 18-4 is arranged in juxtaposition.System 100 can comprise diverter valve 19 (being also known as distributing valve), and its operation is to be divided into the stream entering the 3rd heat exchanger 18-3 and the 4th heat exchanger 18-4 simultaneously by the fluid of discharging from recuperator 18-2.Therefore, the fluid 33 be in temperature T6 of discharging from recuperator 18-2 is inhaled in the 3rd heat exchanger 18-3 and the 4th heat exchanger 18-4.3rd heat exchanger 18-3 by the heat trnasfer of the exhaust 108 from motor 52 to fluid 33, the fluid 29 of source under the temperature T14 higher than temperature T6 side by side.Fluid 29 flows directly to the first expansion stages 20-1.Similarly, the 4th heat exchanger 18-4 is by the heat trnasfer of the exhaust 108 from motor 52 to fluid 33, and displacement fluids 36, then this fluid 36 is drawn to the first expansion stages 20-1.
Although 49. these examples are described two heat exchanger 18-3 and 18-4 and are arranged in juxtaposition by a diverter valve 19, be arranged in juxtaposition by one or more diverter valve more than two heat exchangers, prerequisite is that the fluid 36 being introduced into the first expansion stages 20-1 discharged by each heat exchanger.
50. other examples are directed to the method using three grades of expansion systems in Rankine cycle as described in fig. 1 and 2.
51. Fig. 4 are for making working fluid 12 at the flow chart with the illustrative methods 300 circulated in the Rankine cycle of three grades of expansion systems.In process 302, working fluid 12 is at least heated to partial vapor state.This process can be performed by heat-exchanger rig, such as First Heat Exchanger 18-1, the second heat exchanger 18-2, the 3rd heat exchanger 18-3 or the 4th heat exchanger 18-4 or its any combination.In process 304, working fluid 12 passes through from the first expansion stages 20-1, and the first expansion stages makes working fluid 12 expand and produces useful work from expansion.In process 306, the working fluid 12 of discharging from the first expansion stages 20-1 passes through from the second expansion stages 20-2.Second expansion stages 20-2 produces useful work by making working fluid 12 expand.Then working fluid 12 discharges from the second expansion stages 20-2.In process 308, working fluid 12 is through the 3rd expansion stages 20-3, and the 3rd expansion stages 20-3 produces useful work by making working fluid 12 expand.In process 310, the working fluid 14 being used to be produced by the first expansion stages 20-1, the second expansion stages 20-2 and the 3rd expansion stages 20-3 useful work is condensed to liquid state subsequently, and return course 302.
52. Fig. 5 are for making working fluid 12 at the flow chart with the illustrative methods 200 circulated in the Rankine cycle of three grades of expansion systems.Such as, process 200 can perform according in the system 100 of the second example described in reference diagram 2 above.In this example, the working fluid 36 be under temperature T8 enters the first expansion stages 20-1 (202).In process 202, the pressure and temperature of working fluid 36 passes through from the first expansion stages 20-1 along with working fluid 36 and reduces, and described first expansion stages 20-1 produces the mechanical energy being also called as useful work in literary composition simultaneously.Then first expansion stages 20-1 discharges the working fluid 14 be under temperature T9.Working fluid 14 flows into the second expansion stages 20-1 (204).In process 204, the pressure and temperature of working fluid 14 passes through from the second expansion stages 20-2 produced mechanical energy simultaneously along with working fluid 14 and reduces.Then second expansion stages 20-2 discharges the working fluid 17 be under temperature T12.Working fluid 17 flows into the 3rd expansion stages 20-3 (206).In process 206, the pressure and temperature of working fluid 17 passes through from the 3rd expansion stages 20-3 produced mechanical energy simultaneously along with working fluid 17 and reduces.Then 3rd expansion stages 20-3 discharges the working fluid 21 be under temperature T4.
53. working fluids 21 enter the second heat exchanger or recuperator 18-2 (208).In process 208, the temperature of working fluid 21 is down to temperature T10 by recuperator 18-2.The working fluid 23 be under temperature T10 enters condenser 25 subsequently, and this condenser 25 makes fluid 23 liquefy the working fluid 31 (210) of source under temperature T5 side by side.As shown in Figure 7, the temperature T5 of fluid 31 is substantially identical with the temperature T10 of fluid 23.In process 212, working fluid 31 is by pump 16 pumping.From the working fluid 27 of pump 16 pumping, there is the temperature T13 higher than the temperature T5 of fluid 31, as shown in Figure 7.In process 214, working fluid 27 is heated by recuperator 18-2 and has the temperature of rising.Recuperator 18-2 generation is in the working fluid 33 under the temperature T6 higher than T13.In process 216, working fluid 33 is heated further by the 3rd heat exchanger 18-3 and has the temperature of rising.3rd heat exchanger 18-3 discharge is in the working fluid 35 under the temperature T7 higher than T6.In process 218, working fluid 35 is again heated by the 4th heat exchanger 18-4 and has the temperature of rising.4th heat exchanger 18-4 discharges the working fluid 36 being in the temperature T8 higher than T7.Working fluid 36 is fed back in the 3rd expansion stages 18-3 in process 202, as mentioned above.
54. Fig. 6 are the flow charts for another illustrative methods 200 making working fluid 12 circulate in the Rankine cycle with three grades of expansion systems.Such as, process 200 can perform according in the system 200 of the first example described in reference diagram 1 above.Due to the first example basic simlarity shown in the method in this example and Fig. 8, so being described in this and being incorporated to by reference in this example for the first example.When showing same or similar feature or element, identical reference character will be used as far as possible.The difference that will be mainly limited between the first example and the second example is below described.
55. in this example, and method 200 is also included in the step (220) of the temperature raising working fluid between process 202 and 204 at First Heat Exchanger 18-1 place.In process 220, the working fluid 14 through the first expansion stages 20-1 is introduced into First Heat Exchanger 18-1 to raise its temperature before entering the second expansion stages 20-2.Along with working fluid 14 passes through from First Heat Exchanger 18-1, temperature is elevated to T11 from T9.Therefore, First Heat Exchanger 18-1 discharge is in the working fluid 13 under temperature T11, and working fluid 13 flows into the second expansion stages 20-2 being used for process 204 subsequently.
56.
displacement fluid expander
57. Fig. 7-12 show for the expander in the system shown in Fig. 1-3.Fig. 7 is the side perspective of an example of the displacement fluid expansion stages of the feature of the example of the aspect had as principle according to the present invention.Fig. 8 is the cross section side perspective of the displacement fluid expander shown in Fig. 7.Fig. 9 be have as according to of the present invention away from the side cross-sectional view of another example of displacement fluid expansion stages of feature of example of aspect.Generally speaking, positive displacement energy recycle device 20 relies on the kinetic energy of working fluid 12-1 and static pressure to carry out rotating output shaft 38.When device 20 is used to expand application (such as together with Rankine cycle), from working fluid, extract extra energy via fluid expansion.In these cases, device 20 can be called as expander or expansion gear, as institute's appellation in paragraph below.It is to be understood, however, that device 20 is not limited to the application that working fluid expands in this device.
58. expansion gears 20 have band fluid input 24 and the housing 22 of fluid output 26, by the working fluid 12-1 of fluid output 26 bear pressure drop with by energy trasfer to output shaft 38.Ingress port 24 is configured to allow the working fluid 12-1 be under the first pressure from heat exchanger 18 (illustrating in fig. 1-3) to enter, and outlet port 26 is configured to discharge working fluid 12-2 under the second pressure lower than the first pressure.Output shaft 38 is driven by the rotor 30,32 of the first and second staggered counterrotatings of synchronized links, and described rotor is arranged in the cavity 28 of housing 22.That each rotor 30,32 has torsion or arrange spirally along the length of rotor 30,32 blade.When rotor 30,32 rotates, blade againsts the inner side seal operation fluid 12-1 at least in part of housing, and the now expansion of working fluid 12-1 only occurs in system the degree of the leakage permission representing poor efficiency.Contrary with some are changed working fluid volume expansion gear when fluid seals, because working fluid 12-1 crosses the length of rotor 30,32, so the volume limited between the inner side of the housing 22 of blade and device 20 is constant.Therefore, expansion gear 20 can be called as " positive displacement arrangements ", because the working fluid volume being sealed or partly seal does not change.
59. as Figure 10 in addition shown in, each rotor 30,32 has four blades 30-1,30-2,30-3 and 30-4 for rotor 30, and has four blades 32-1,32-2,32-3 and 32-4 for rotor 32.Although show four blades to each rotor 30 and 32, each rotor in two rotors can have any amount of blade being equal to or greater than 2.In addition, two rotors 30 are identical with the blade quantity of 32.This and common rotating screw devices are formed with other structure with the rotating equipment (such as, have the male rotor of " n " individual blade and have the female rotor of " n+1 " individual blade) formed similarly of the blade of varying number and contrast.In addition, a distinctive feature of expansion gear 20 is: rotor 30 is identical with 32, and its rotor 30,32 is relatively arranged so that, when observing from an axial end, the vane clockwise of a rotor reverses, and the blade of the rotor of engagement reverses counterclockwise.Relative to ingress port 24 and therefore therefore, when a blade of rotor 30 is as advanced relative to ingress port 24 in blade 30-1, the blade of rotor 32 is posterior relative to the stream of pressurized working fluid 12-1 as blade 30-2.
60. as shown in the figure, and the first rotor 30 and the second rotor 32 are fixed on respective rotor shaft, and the first rotor is fixed on output shaft 38 and the second rotor is fixed on axle 40.Each rotor shaft 38,40 is mounted to rotate in one group of bearing (not shown) around axis X 1, X2 respectively.Be to be noted that axis X 1 and X2 are roughly parallel to each other.The first rotor 30 and the second rotor 32 interlock and engage so that rotation integral with one another continuously.
61. the first rotors 30 and the second rotor 32 interlock and engage so that rotation integral with one another continuously.Referring again to Fig. 9, expander 20 also comprises the timing gear 42 and 44 of engagement, and wherein, timing gear 42 is fixed into and rotates together with rotor 30, and timing gear 44 is fixed into and rotates together with rotor 32.Timing gear 42,44 is also configured to the relative position maintaining rotor 30,32, and make the contact prevented between rotor 30,32 between rotor, this contact can cause the large range damage of rotor 30,32.Specifically, during rotation the close tolerance between rotor 30,32 is maintained by timing gear 42,44.Because rotor 30,32 is non-contacting, so the operation of expansion gear 20 does not need the oiling agent in fluid 12, formed with common rotating screw devices and other rotating equipment formed similarly with the rotor blade contacted with each other and contrast.
62. bear the expansion from the working fluid 12-1 of higher first pressure to the working fluid 12-2 of lower second pressure due to working fluid, and output shaft 38 is driven rotation by working fluid 12.As seen in addition in figure 9 and in figure 10, output shaft 38 extends beyond the border of housing 22.Therefore, output shaft 38 is configured to (occur in the rotor cavity 28 of this expansion between ingress port 24 and outlet end 26) to obtain the merit or power that are produced by expander 20 between the phase of expansion of working fluid 12, and described merit is shifted as Driving Torque from expander 20.Although output shaft 38 is depicted as operatively be connected to the first rotor 30, in replacement scheme, output shaft 38 operatively can be connected to the second rotor 32.Output shaft 38 can be connected to motor 52, makes the energy from waste gas can by recapture.63. in one of the geometrical construction of expansion gear 20 in, in the geometrical construction that each rotor blade 30-1 to 30-4 and 32-1 to 32-4 has, the length 34 that the torsion of each in the first rotor 30 and the second rotor 32 is mated substantially along them is constant.As Figure 11 schematically shows, a parameter of blade geometry structure is helix angle HA.By the mode of definition, it should be understood that " helix angle " of the rotor blade mentioned by hereafter refers to the helix angle at pitch diameter PD (or pitch circle) place at rotor 30 and 32.Term " pitch diameter " and the technician of identification to gear and rotor field thereof understand very well, discuss no longer further at this.As used herein, helix angle HA can calculate as follows: helix angle (HA)=(180/.pi.*arctan (PD/Lead)), wherein, and the pitch diameter of PD=rotor blade; And Lead=blade completes the length of blade needed for 360 degree of torsions.Should point out, Lead is the function of the corresponding torsion angle of blade 30,32 and length L1, L2.For those skilled in the art it is known that torsion angle is the angle displacement of blade, in units of spending, in the middle of its front end edge length of blade L occurred in from the rear end of rotor to rotor " advances ".As shown in the figure, torsion angle is about 120 degree, but the angle of torsion angle can be less or more, such as 160 degree.
64. expander geometrical construction another in, as Fig. 9 can schematically find out, ingress port 24 includes bicker 24-1.In one example, Inlet cone angle 24-1 is defined as cardinal principle or the average angle of the internal surface 24a (such as front side internal surface) of ingress port 24.In one example, Inlet cone angle 24-1 is defined as the angle of the general center line of ingress port 24, such as illustrated in fig. 9.In one example, Inlet cone angle 24-1 is defined as: owing to contacting with front side internal surface 24a, enter the direction substantially obtained of the working fluid 12-1 of rotor 30,32, as seen in Figure 9.As shown in the figure, Inlet cone angle 24-1 had both been not orthogonal to spin axis X1, X2 of being also not parallel to rotor 30,32.Therefore, the front side internal surface 24a of ingress port 24 makes the major component of working fluid 12-1 become on the direction at tilt angle to be formed at spin axis X1, the X2 relative to rotor 30,32, thus is roughly parallel to Inlet cone angle 24-1.
65. in addition, and as shown in Figure 9, ingress port 24 can be shaped so that, working fluid 12-1 is drawn towards first axial end 30a, 32a of rotor 30,32, and be drawn towards the leading surface of rotor blade and rear along face (below illustrate) from side direction.It is to be understood, however, that Inlet cone angle 24-1 can be roughly parallel to or be approximately perpendicular to axis X 1, X2, but it is expected to efficient loss for some rotor configuration.In addition, be to be noted that ingress port 24 can be shaped as and narrow towards inlet opens 24b, as shown in Figure 9.
66. with reference to Figure 12, and can find out, ingress port 24 has the width W of the combined diameter distance being slightly less than rotor 30,32.The combined rotor diameter distance equaled between axis X 1 and X2 adds the twice of the distance of the end from cener line X1 or X2 to respective vanes.In some instances, width W is equal to or greater than combined rotor diameter.
67. expander geometrical construction another in, as Fig. 9 can schematically find out, ingress port 26 comprises exit angle 26-1.In one example, exit angle 26-1 is defined as cardinal principle angle or the average angle of the internal surface 26a of outlet end 26.In one example, exit angle 26-1 is defined as the angle of the general center line of outlet end 26, such as in fig .9 shown in.In one example, exit angle 26-1 is defined as the general direction that the working fluid 12-2 that leaves rotor 30,32 produces owing to contacting with internal surface 26a, as found out in fig .9.As shown in the figure, exit angle 26-1 had both been not orthogonal to spin axis X1, X2 of being also not parallel to rotor 30,32.Therefore, the internal surface 26a of outlet end 26 receives the working fluid 12-2 left from rotor 30,32 with tilt angle, this tilt angle can reduce the back pressure at outlet end 26 place.In one example, Inlet cone angle 24-1 is roughly equal with exit angle 26-1 or parallel, as shown in Figure 9.In one example, Inlet cone angle 24-1 and exit angle 26-1 relative to each other tilts.It should be understood that exit angle 26-1 can be approximately perpendicular to axis X 1, X2, although can the loss of expectability generation efficiency for some rotor configuration.Be also pointed out that exit angle 26-1 can perpendicular to axis X 1, X2.As constructed, the orientation of outlet port 26-1 and size are asserted and make, and the working fluid 12-2 left can as far as possible easily and promptly discharge each rotor cavity 28, thus reduces back pressure as much as possible.The outputting power of axle 38 is maximized to by exporting the degree that the back pressure that causes can be minimum, makes working fluid can be become the pressure working fluid at condenser place by promptly discharge.
68. by coordinating the geometrical construction of Inlet cone angle 24-1 and the geometrical construction of rotor 30,32, and the efficiency of expander 20 can be optimized.Such as, rotor 30,32 helix angle HA and Inlet cone angle 24-1 can in complementary fashion together be configured to.Because ingress port 24 guides working fluid 12-1 to the leading surface of each rotor 30,32 and rear along face, therefore working fluid 12-1 performs both positive work and negative work on expander 20.
69. for ease of illustrating, Figure 10 illustrates that blade 30-1,30-4,32-1 and 32-2 are all exposed to working fluid 12-1 by the opening 24b of ingress port.Each blade all has leading surface and rear along face, and the two is exposed to working fluid at multiple turning point places of associated rotor.Leading surface is the side of the forefront of the blade when rotor rotates along direction R1, R2, is then the side facing to leading surface of blade along face.Such as, rotor 30 rotates along direction R1, cause side 30-1a as the leading surface of blade 30-1 thus and side 30-1b as rear along face.When rotor 32 rotates along the direction R2 contrary with direction R1, leading surface and rear be mirror image along face, make side 32-2a be the leading surface of blade 32-2, and side 32-2b is rear along face.
70. put it briefly, and working fluid 12-1 from by impinging upon the rear along face of blade during ingress port opening 24b, and performs forward work at them on each rotor 30,32.For the use of term " positive work ", it means that working fluid 12-1 causes rotor to rotate along required direction: direction R1 is used for rotor 30 and direction R2 is used for rotor 32.As shown in the figure, working fluid 12-1 by carrying out operating positive work to be applied to the rear along on the 32-2b of face of rotor 32-2, such as, in surface portion 47.What positive work was also applied to rotor 30-1 by working fluid 12-1 delays on surperficial 30-4b, such as, in surface portion 46.But, working fluid 12-1 also at them from impinging upon the leading surface of blade by during ingress port opening 24b, such as surperficial 30-1 and 32-1, makes to perform negative work thus on each rotor 30,32.For the use of term " negative work ", it means that working fluid 12-1 makes rotor rotate along the opposite direction of required direction R1, R2.
71. therefore, expect rotor 30,32 to be shaped and directed and ingress port 24 is shaped and is orientated and make the rear along face of working fluid 12-1 impact blades as much as possible, and the least possible working fluid 12-1 clashes into forward position blade, can perform the highest clean positive work by expander 20.
72. for the efficiency of optimization expander 20 and a kind of advantageous configuration of clean positive work are, the rotor blade pitch angle HA of about 35 degree and the Inlet cone angle 24-1 of about 30 degree.Such configuration is operating as the rear impingement region along face maximized on blade, minimizes the impingement region of the leading surface of blade simultaneously.In one example, helix angle is between about 25 degree and about 40 degree.In one example, within Inlet cone angle 24-1 is set as being in (the adding deduct) 15 degree of helix angle.In one example, helix angle is between about 25 degree and about 40 degree.In one example, within Inlet cone angle 24-1 is set as being in (the adding deduct) 15 degree of helix angle HA.In one example, helix angle is between about 25 degree and about 40 degree.In one example, within Inlet cone angle 24-1 is set as being in (the adding deduct) 15 degree of helix angle.In one example, within Inlet cone angle is set as being in (the adding deduct) 10 degree of helix angle.In one example, within Inlet cone angle 24-1 is set as being in (the adding deduct) 5 degree of helix angle HA.In one example, within Inlet cone angle 24-1 is set as being in (the adding deduct) 1 15 of helix angle HA, and in one example, within Inlet cone angle 24-1 is in 10 of helix angle.Inlet cone angle and helix angle also can be other values, and do not depart from the concept expressed at this.But, have been found that when Inlet cone angle and helix angle value not fully close to, significant decrease in efficiency (such as, the decline of 10-15%) may be there is.
73.
rankine cycle operates
74. Figure 13 show the chart 48 describing representational Rankine cycle, and this Rankine cycle is applicable to the system 100 as described with reference to figure 1-6.Chart 48 depicts the different phase of Rankine cycle, and it illustrates the degree centigrade indicated relative to entropy " S ", and wherein, entropy is defined as energy (in Kilojoule) divided by Kelvin temperature and further divided by kilogram-mass (kJ/kg*K).Rankine cycle shown in Fig. 7 is in particular the organic Rankine bottoming cycle (ORC) of closed loop, it can use organic polymer amount working fluid, and this working fluid has the liquid-vapour phase occurred under the water-gas phase than classical Rankine cycle changes low temperature and becomes or boiling point.Therefore, within system 100, working fluid 12 can be solvent, such as ethanol, pentane or toluene.
75. in the chart 48 of Figure 13, and term " Q " represents the flow direction or the hot-fluid from system 100, and is typically expressed as the energy of unit time.Term " W " represents mechanical output that is that consumed by system 100 or that be supplied to system 100, and is also typically expressed as the energy of unit time.As can be seen from Figure 13 in addition, have in ORC four different processes or the stage 48-1,48-2,48-3 and 48-4.During stage 48-1, the working fluid 12 of wet vapor form enters and by condenser 25, working fluid is condensed to become saturated liquids at a constant temperature wherein.After stage 48-1, working fluid 12 delivers to high pressure by pump 16 from low pressure pump during stage 48-2.During stage 48-2, working fluid 12 is in liquid condition.
76. working fluids are transferred to stage 48-3 from stage 48-2.During stage 48-3, the working fluid 12 of pressurization enters and by heat exchanger 18, heated to become two-phase fluid by external heat source under a constant at this place's working fluid, that is, liquid is together with steam.Working fluid 12 is transferred to stage 48-4 from stage 48-3.During stage 48-4, the working fluid 12 of two-phase fluid form expands through expander 20, produces useful work or power.The expansion of the working fluid 12 evaporated by the part of expander 20 reduces the temperature and pressure of two-phase fluid, makes the extra condensation that two-phase working fluid 12 may occur.After stage 48-4, working fluid 12 turns back to the condenser 25 at stage 48-1, and at this some place, circulation completes subsequently and usually will restart.
77. usually, and Rankine cycle adopts the turbo machine being configured to working fluid is expanded during stage 48-4.In this case, actual Rankine cycle needs overheated ebullator to enter overheat range to make working fluid, therefrom to remove or to evaporate all liquid in addition.This extra superheating process normally needs, so that any liquid remained in working fluid can not accumulate in turbo machine place thus cause the burn into spot corrosion of turbine bucket and final damage.As shown in the figure, the feature of the ORC of Figure 13 is, the subsidiary superheating process not having this overheated ebullator and evaporate from working fluid needed for all liq.Because expander 20 is configured to the fact of the wrong rotor arrangement of double cross, above-mentioned omission allows, and the wrong rotor arrangement of described double cross can not be subject to the adverse effect that there is liquid in working fluid 12.In addition, the existence of this liquid benefited from by expander 20, and this is mainly because by the gap between sealing the first rotor 30 and the second rotor 32 and between rotor and housing 22, residual liquid trends towards the operating efficiency improving expander.Therefore, when the expander 20 in system 100 produces useful work, the working fluid 12 in expander presents two-phase, that is, liquid-vapour, and the transformation efficiency of ORC is improved.It is to be understood, however, that recovering device 20 may be used for relating in the configuration of overheated gas.
78. in addition, the expander that can size be used within system 100 less, exports to reach required merit.Efficiency will never more than the Carnot efficiency of 63%, because this is maximum Carnot efficiency eff=l-Tcold/Thot.Working fluid may be ethanol, and it has the maximum temperature 350 DEG C before starting to decompose.The efficiency of expander will be less than the peak efficiencies of turbo machine, but on larger range of flow, efficiency area (efficiencyislands) is significantly greater than turbine expander, and the overall efficiency therefore circulated is larger.79. each examples above-mentioned provide only by the mode illustrated and should not be interpreted as limiting attached claim.Those skilled in the art will easily expect the various modifications and changes can made when not following the exemplary embodiment and application that illustrate and describe herein and not departing from true spirit and the scope of attached claim.
Claims (amendment according to treaty the 19th article)
1., for producing a method for mechanical work via closed loop Rankine cycle, described method comprises:
By working fluid heats at least part of vapor state;
By described working fluid from the first expansion stages by time make described expansion of working fluid come described first expansion stages produce useful work;
By described working fluid from the second expansion stages by time make described expansion of working fluid come described second expansion stages produce useful work;
By described working fluid from the 3rd expansion stages by time make described expansion of working fluid come described 3rd expansion stages produce useful work; And
Described working fluid is made to be condensed to liquid state.
2., for producing a method for mechanical work via closed loop Rankine cycle, described method comprises:
Described working fluid is passed through, to raise the temperature of described working fluid from heat-exchanger rig;
Described working fluid is passed through, to reduce the temperature and pressure of described working fluid and to form the 3rd mechanical work from the first displacement fluid expansion stages;
Described working fluid is passed through, to reduce the temperature and pressure of described working fluid and to form the first mechanical work from the second displacement fluid expansion stages;
Described working fluid is passed through, to reduce the temperature and pressure of described working fluid and to form the second mechanical work from the 3rd displacement fluid expansion stages;
Make described working fluid condensation; And
Described working fluid is made to return described first displacement fluid expansion stages.
3. method according to claim 2, wherein, the step that described working fluid is passed through from described heat-exchanger rig comprises:
The hot-fluid from power plant is received by described heat-exchanger rig; And
By described heat-exchanger rig, the heat from described hot-fluid is delivered to described working fluid.
4. method according to claim 2, wherein, the step that described working fluid is passed through from described heat-exchanger rig comprises: provide the First Heat Exchanger be arranged between described first displacement fluid expansion stages and described second displacement fluid expansion stages,
Described method also comprises:
Described working fluid is passed through from described First Heat Exchanger, to raise the temperature of described working fluid, wherein, described First Heat Exchanger be configured to receive from power plant hot-fluid and the heat from described hot-fluid is delivered to described working fluid.
5. method according to claim 4, is also included in and after working fluid described in condensation, described working fluid is passed through from the second heat exchanger, to raise the temperature of described working fluid.
6. method according to claim 5, wherein, the step that described working fluid is passed through from described heat-exchanger rig comprises: provide the downstream being arranged in described second heat exchanger to receive the 3rd heat exchanger from the working fluid of described second heat exchanger,
Described method also comprises:
Described working fluid is passed through from described 3rd heat exchanger, and to raise the temperature of described working fluid, wherein, described 3rd heat exchanger construction becomes receive the hot-fluid from power plant and the heat from described hot-fluid is delivered to described working fluid.
7. method according to claim 5, wherein, the step that described working fluid is passed through from described heat-exchanger rig comprises: provide the downstream being arranged in described second heat exchanger to receive the 3rd heat exchanger from the working fluid of described second heat exchanger,
Described method also comprises:
Described working fluid is passed through from described 3rd heat exchanger, and to raise the temperature of described working fluid, wherein, described 3rd heat exchanger construction becomes receive the hot-fluid from described First Heat Exchanger and the heat from described hot-fluid is delivered to described working fluid.
8. method according to claim 6, wherein, the step that described working fluid is passed through from described heat-exchanger rig comprises: provide the downstream being arranged in described 3rd heat exchanger to receive the 4th heat exchanger from the working fluid of described 3rd heat exchanger,
Described method also comprises:
Described working fluid is passed through from described 4th heat exchanger, and to raise the temperature of described working fluid, wherein, described 4th heat exchanger construction becomes receive the hot-fluid from power plant and the heat from described hot-fluid is delivered to described working fluid.
9., for producing a system for mechanical work via closed loop Rankine cycle, described system comprises:
Produce hot-fluid and there are the power plant of the heat outlet left for described hot-fluid;
Be configured to the heat-exchanger rig heat from described hot-fluid being delivered to working fluid stream;
Be configured to receive the first displacement fluid expansion stages from the working fluid stream of described heat-exchanger rig;
Be configured to receive the second displacement fluid expansion stages from the working fluid stream of described first displacement fluid expansion stages; With
Be configured to receive the 3rd displacement fluid expansion stages from the working fluid stream of described second displacement fluid expansion stages;
Wherein, each in described first displacement fluid expansion stages, the second displacement fluid expansion stages and the 3rd displacement fluid expansion stages is all configured to by the raw mechanical work of working fluid miscarriage.
10. system according to claim 9, also comprises the working fluid that is configured to receive from described 3rd displacement fluid expansion stages and makes the condenser of described working fluid condensation.
11. systems according to claim 10, also comprise and are configured to receive the working fluid from described condenser and the pump of working fluid described in pumping in the circulating cycle.
12. systems according to claim 10, wherein, described heat-exchanger rig comprises First Heat Exchanger, described First Heat Exchanger is configured to: receive the hot-fluid from described power plant, receive the working fluid from described first displacement fluid expansion stages, heat from described hot-fluid is delivered to working fluid stream, and described working fluid stream is supplied to described second displacement fluid expansion stages.
13. systems according to claim 10, wherein, described heat-exchanger rig comprises the second heat exchanger being configured to receive the working fluid of discharging from described second displacement fluid expansion stages, wherein, the working fluid leaving described second heat exchanger flows in described condenser, and described second heat exchanger is also configured to receive the working fluid of discharging from described condenser and the heat of the working fluid of discharging since described 3rd displacement fluid expansion stages is in the future delivered to the working fluid of discharging from described condenser.
14. systems according to claim 13, wherein, described heat-exchanger rig comprises the 3rd heat exchanger being configured to receive the hot-fluid from described First Heat Exchanger and the working fluid from described second heat exchanger, and described 3rd heat exchanger construction becomes the working fluid being delivered to by the heat from described hot-fluid and discharging from described second heat exchanger.
15. systems according to claim 14, wherein, described heat-exchanger rig comprises the 4th heat exchanger being configured to receive from the hot-fluid of described power plant and the working fluid from described 3rd heat exchanger, and described 4th heat exchanger construction becomes the working fluid being delivered to by the heat from described hot-fluid and discharging from described 3rd heat exchanger.
16. systems according to claim 15, wherein, described first displacement fluid expansion stages is arranged between described 4th heat exchanger and described First Heat Exchanger, and be configured to receive from described 4th heat exchanger discharge working fluid and described working fluid is discharged to described First Heat Exchanger.
Claims (16)
1., for producing a method for mechanical work via closed loop Rankine cycle, described method comprises:
By working fluid heats at least part of vapor state;
By described working fluid from the first expansion stages by time make described expansion of working fluid come described first expansion stages produce useful work;
By described working fluid from the second expansion stages by time make described expansion of working fluid come described second expansion stages produce useful work;
By described working fluid from the 3rd expansion stages by time make described expansion of working fluid come described 3rd expansion stages produce useful work; And
Described working fluid is made to be condensed to liquid state.
2., for producing a method for mechanical work via closed loop Rankine cycle, described method comprises:
Described working fluid is passed through, to raise the temperature of described working fluid from heat-exchanger rig;
Described working fluid is passed through, to reduce the temperature and pressure of described working fluid and to form the 3rd mechanical work from the first displacement fluid expansion stages;
Described working fluid is passed through, to reduce the temperature and pressure of described working fluid and to form the first mechanical work from the second displacement fluid expansion stages;
Described working fluid is passed through, to reduce the temperature and pressure of described working fluid and to form the second mechanical work from the 3rd displacement fluid expansion stages;
Make described working fluid condensation; And
Described working fluid is made to return described first displacement fluid expansion stages.
3. method according to claim 2, wherein, the step that described working fluid is passed through from described heat-exchanger rig comprises:
The hot-fluid from power plant is received by described heat-exchanger rig; And
By described heat-exchanger rig, the heat from described hot-fluid is delivered to described working fluid.
4. method according to claim 2, wherein, the step that described working fluid is passed through from described heat-exchanger rig comprises: provide the First Heat Exchanger be arranged between described first displacement fluid expansion stages and described second displacement fluid expansion stages,
Described method also comprises:
Described working fluid is passed through from described First Heat Exchanger, to raise the temperature of described working fluid, wherein, described First Heat Exchanger be configured to receive from power plant hot-fluid and the heat from described hot-fluid is delivered to described working fluid.
5. method according to claim 4, is also included in and after working fluid described in condensation, described working fluid is passed through from the second heat exchanger, to raise the temperature of described working fluid.
6. method according to claim 5, wherein, the step that described working fluid is passed through from described heat-exchanger rig comprises: provide the downstream being arranged in described second heat exchanger to receive the 3rd heat exchanger from the working fluid of described second heat exchanger,
Described method also comprises:
Described working fluid is passed through from described 3rd heat exchanger, and to raise the temperature of described working fluid, wherein, described 3rd heat exchanger construction becomes receive the hot-fluid from power plant and the heat from described hot-fluid is delivered to described working fluid.
7. method according to claim 5, wherein, the step that described working fluid is passed through from described heat-exchanger rig comprises: provide the downstream being arranged in described second heat exchanger to receive the 3rd heat exchanger from the working fluid of described second heat exchanger,
Described method also comprises:
Described working fluid is passed through from described 3rd heat exchanger, and to raise the temperature of described working fluid, wherein, described 3rd heat exchanger construction becomes receive the hot-fluid from described First Heat Exchanger and the heat from described hot-fluid is delivered to described working fluid.
8. method according to claim 6, wherein, the step that described working fluid is passed through from described heat-exchanger rig comprises: provide the downstream being arranged in described 3rd heat exchanger to receive the 4th heat exchanger from the working fluid of described 3rd heat exchanger,
Described method also comprises:
Described working fluid is passed through from described 4th heat exchanger, and to raise the temperature of described working fluid, wherein, described 4th heat exchanger construction becomes receive the hot-fluid from power plant and the heat from described hot-fluid is delivered to described working fluid.
9., for producing a system for mechanical work via closed loop Rankine cycle, described system comprises:
Produce hot-fluid and there are the power plant of the heat outlet left for described hot-fluid;
Be configured to the heat-exchanger rig heat from described hot-fluid being delivered to working fluid stream;
Be configured to receive the first displacement fluid expansion stages from the working fluid stream of First Heat Exchanger;
Be configured to receive the second displacement fluid expansion stages from the working fluid stream of described first displacement fluid expansion stages; With
Be configured to receive the 3rd displacement fluid expansion stages from the working fluid stream of described second displacement fluid expansion stages;
Wherein, each in described first displacement fluid expansion stages, the second displacement fluid expansion stages and the 3rd displacement fluid expansion stages is all configured to by the raw mechanical work of working fluid miscarriage.
10. system according to claim 9, also comprises the working fluid that is configured to receive from described 3rd displacement fluid expansion stages and makes the condenser of described working fluid condensation.
11. systems according to claim 10, also comprise and are configured to receive the working fluid from described condenser and the pump of working fluid described in pumping in the circulating cycle.
12. systems according to claim 10, wherein, described heat-exchanger rig comprises First Heat Exchanger, described First Heat Exchanger is configured to: receive the hot-fluid from described power plant, receive the working fluid from described first displacement fluid expansion stages, heat from described hot-fluid is delivered to working fluid stream, and described working fluid stream is supplied to described second displacement fluid expansion stages.
13. systems according to claim 10, wherein, described heat-exchanger rig comprises the second heat exchanger being configured to receive the working fluid of discharging from described second displacement fluid expansion stages, wherein, the working fluid leaving described second heat exchanger flows in described condenser, and described second heat exchanger is also configured to receive the working fluid of discharging from described condenser and the heat of the working fluid of discharging since described 3rd displacement fluid expansion stages is in the future delivered to the working fluid of discharging from described condenser.
14. systems according to claim 13, wherein, described heat-exchanger rig comprises the 3rd heat exchanger being configured to receive the hot-fluid from described First Heat Exchanger and the working fluid from described second heat exchanger, and described 3rd heat exchanger construction becomes the working fluid being delivered to by the heat from described hot-fluid and discharging from described second heat exchanger.
15. systems according to claim 14, wherein, described heat-exchanger rig comprises the 4th heat exchanger being configured to receive from the hot-fluid of described power plant and the working fluid from described 3rd heat exchanger, and described 4th heat exchanger construction becomes the working fluid being delivered to by the heat from described hot-fluid and discharging from described 3rd heat exchanger.
16. systems according to claim 15, wherein, described first displacement fluid expansion stages is arranged between described 4th heat exchanger and described First Heat Exchanger, and be configured to receive from described 4th heat exchanger discharge working fluid and described working fluid is discharged to described First Heat Exchanger.
Applications Claiming Priority (7)
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| US201361757533P | 2013-01-28 | 2013-01-28 | |
| US61/757,533 | 2013-01-28 | ||
| US201361810579P | 2013-04-10 | 2013-04-10 | |
| US61/810,579 | 2013-04-10 | ||
| US201361816143P | 2013-04-25 | 2013-04-25 | |
| US61/816,143 | 2013-04-25 | ||
| PCT/US2014/013393 WO2014117152A1 (en) | 2013-01-28 | 2014-01-28 | Volumetric energy recovery system with three stage expansion |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN105209724A true CN105209724A (en) | 2015-12-30 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201480017829.0A Pending CN105051329A (en) | 2013-01-28 | 2014-01-28 | Multi-stage volumetric fluid expansion device |
| CN201480017926.XA Pending CN105209724A (en) | 2013-01-28 | 2014-01-28 | Volumetric energy recovery system with three stage expansion |
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| CN201480017829.0A Pending CN105051329A (en) | 2013-01-28 | 2014-01-28 | Multi-stage volumetric fluid expansion device |
Country Status (4)
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| US (2) | US20150330257A1 (en) |
| EP (2) | EP2948647B1 (en) |
| CN (2) | CN105051329A (en) |
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Families Citing this family (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20140260245A1 (en) * | 2013-03-15 | 2014-09-18 | Eaton Corporation | Volumetric energy recovery device with variable speed drive |
| ES2841131T3 (en) * | 2013-09-25 | 2021-07-07 | Siemens Energy Global Gmbh & Co Kg | Arrangement and method for utilization of waste heat |
| WO2016032737A1 (en) * | 2014-08-28 | 2016-03-03 | Eaton Corporation | Optimized performance strategy for a multi-stage volumetric expander |
| CA2962461C (en) * | 2014-09-25 | 2022-06-21 | Nuhn Industries Ltd. | Fluid pump with multiple pump heads |
| EP3032048A1 (en) | 2014-12-09 | 2016-06-15 | Eaton Corporation | Organic rankine cycle system with lubrication circuit |
| WO2016109551A1 (en) * | 2014-12-30 | 2016-07-07 | Eaton Corporation | Optimal expander outlet porting |
| WO2016187429A1 (en) * | 2015-05-19 | 2016-11-24 | Eaton Corporation | Configuration for optimized waste heat recovery |
| EP3118424B1 (en) * | 2015-07-16 | 2020-05-20 | Orcan Energy AG | Control of orc processes by injection of un-vaporized fluids |
| US20190113035A1 (en) | 2016-03-09 | 2019-04-18 | Eaton Intelligent Power Limited | Optimized energy recovery device rotor |
| EP3330499B1 (en) | 2016-12-05 | 2023-08-23 | Orcan Energy AG | System and method for energy recovery in industrial facilities |
| DE102017121954A1 (en) * | 2017-09-21 | 2019-03-21 | GasNet s.r.o. | Screw expanders and methods for generating mechanical energy by expanding a working fluid |
| CN111237734A (en) * | 2020-03-11 | 2020-06-05 | 西安热工研究院有限公司 | Three-stage regenerative intermediate reheating supercritical carbon dioxide coal-fired power generation system and operation method |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2010974A (en) * | 1977-12-05 | 1979-07-04 | Fiat Spa | Heat Recovery System |
| US20030012675A1 (en) * | 2000-02-18 | 2003-01-16 | Vratislav Perna | Equipment with mutually interacting spiral teeth |
| US20090000299A1 (en) * | 2007-06-29 | 2009-01-01 | General Electric Company | System and method for recovering waste heat |
| CN101377135A (en) * | 2007-08-31 | 2009-03-04 | 通用电气公司 | Electric generation system with exhaust temperature adjusting deivce and method for controlling exhaust temperature |
| EP2522828A2 (en) * | 2011-05-13 | 2012-11-14 | General Electric Company | Organic rankine cycle systems using waste heat from charge air cooling |
Family Cites Families (22)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3611718A (en) * | 1970-05-05 | 1971-10-12 | Treadwell Corp | Waste heat steam generating cycle |
| US3908381A (en) * | 1974-11-20 | 1975-09-30 | Sperry Rand Corp | Geothermal energy conversion system for maximum energy extraction |
| US4300353A (en) * | 1975-07-24 | 1981-11-17 | Ridgway Stuart L | Vehicle propulsion system |
| US4090362A (en) * | 1976-08-23 | 1978-05-23 | Bourque Robert F | External combustion power cycle and engine with combustion air preheating |
| US5000003A (en) * | 1989-08-28 | 1991-03-19 | Wicks Frank E | Combined cycle engine |
| US5241817A (en) * | 1991-04-09 | 1993-09-07 | George Jr Leslie C | Screw engine with regenerative braking |
| US5327987A (en) * | 1992-04-02 | 1994-07-12 | Abdelmalek Fawzy T | High efficiency hybrid car with gasoline engine, and electric battery powered motor |
| NL9401700A (en) * | 1994-10-14 | 1996-05-01 | Albert Bakker | Hot gas engine and / / compressor unit. |
| US5555731A (en) * | 1995-02-28 | 1996-09-17 | Rosenblatt; Joel H. | Preheated injection turbine system |
| US5605124A (en) * | 1995-11-06 | 1997-02-25 | Morgan; Christopher K. | Rotary screw internal combustion engine |
| US20070157659A1 (en) * | 2006-01-10 | 2007-07-12 | Mcphail Richard Jr | Multi-stage refrigerant turbine |
| US20100192574A1 (en) * | 2006-01-19 | 2010-08-05 | Langson Richard K | Power compounder |
| US7748210B2 (en) * | 2008-07-31 | 2010-07-06 | General Electric Company | System and method for use in a combined or rankine cycle power plant |
| US20110209473A1 (en) * | 2010-02-26 | 2011-09-01 | Jassin Fritz | System and method for waste heat recovery in exhaust gas recirculation |
| CN101852092B (en) * | 2010-04-23 | 2012-05-23 | 马重芳 | Power system of single-screw expansion engine as pneumatic automobile engine |
| DE102010034230A1 (en) * | 2010-08-07 | 2012-02-09 | Daimler Ag | Expansion device for use in a working fluid circuit and method for operating an expansion device |
| US8464697B2 (en) | 2010-08-13 | 2013-06-18 | Eaton Corporation | Integrated clutch supercharger |
| ITMI20110684A1 (en) * | 2011-04-21 | 2012-10-22 | Exergy Orc S R L | PLANT AND PROCESS FOR ENERGY PRODUCTION THROUGH ORGANIC CYCLE RANKINE |
| CN202250242U (en) * | 2011-09-08 | 2012-05-30 | 上海汉钟精机股份有限公司 | Open-type double screw decompressor |
| CN102434236A (en) * | 2011-11-17 | 2012-05-02 | 重庆川然节能技术有限公司 | Threaded rod expansion/centripetal turbine low-parameter waste heat combined generator unit |
| CN202391502U (en) * | 2011-11-17 | 2012-08-22 | 重庆川然节能技术有限公司 | Screw expansion/centripetal turbine low-parameter waste-heat combined generator set |
| CN103321778A (en) | 2012-02-29 | 2013-09-25 | 伊顿公司 | Volumetric energy recovery device and systems |
-
2014
- 2014-01-28 WO PCT/US2014/013393 patent/WO2014117152A1/en active Application Filing
- 2014-01-28 EP EP14704724.5A patent/EP2948647B1/en not_active Not-in-force
- 2014-01-28 WO PCT/US2014/013401 patent/WO2014117159A1/en active Application Filing
- 2014-01-28 CN CN201480017829.0A patent/CN105051329A/en active Pending
- 2014-01-28 EP EP14703515.8A patent/EP2981684A1/en not_active Withdrawn
- 2014-01-28 CN CN201480017926.XA patent/CN105209724A/en active Pending
-
2015
- 2015-07-28 US US14/810,726 patent/US20150330257A1/en not_active Abandoned
- 2015-07-28 US US14/810,712 patent/US20150330258A1/en not_active Abandoned
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2010974A (en) * | 1977-12-05 | 1979-07-04 | Fiat Spa | Heat Recovery System |
| US20030012675A1 (en) * | 2000-02-18 | 2003-01-16 | Vratislav Perna | Equipment with mutually interacting spiral teeth |
| US20090000299A1 (en) * | 2007-06-29 | 2009-01-01 | General Electric Company | System and method for recovering waste heat |
| CN101377135A (en) * | 2007-08-31 | 2009-03-04 | 通用电气公司 | Electric generation system with exhaust temperature adjusting deivce and method for controlling exhaust temperature |
| EP2522828A2 (en) * | 2011-05-13 | 2012-11-14 | General Electric Company | Organic rankine cycle systems using waste heat from charge air cooling |
Also Published As
| Publication number | Publication date |
|---|---|
| US20150330257A1 (en) | 2015-11-19 |
| EP2948647A1 (en) | 2015-12-02 |
| WO2014117152A1 (en) | 2014-07-31 |
| US20150330258A1 (en) | 2015-11-19 |
| EP2948647B1 (en) | 2016-11-16 |
| WO2014117159A1 (en) | 2014-07-31 |
| CN105051329A (en) | 2015-11-11 |
| WO2014117152A4 (en) | 2014-09-12 |
| EP2981684A1 (en) | 2016-02-10 |
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