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WO2016032737A1 - Stratégie d'efficacité optimisée pour un détendeur volumétrique multi-étages - Google Patents

Stratégie d'efficacité optimisée pour un détendeur volumétrique multi-étages Download PDF

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Publication number
WO2016032737A1
WO2016032737A1 PCT/US2015/044529 US2015044529W WO2016032737A1 WO 2016032737 A1 WO2016032737 A1 WO 2016032737A1 US 2015044529 W US2015044529 W US 2015044529W WO 2016032737 A1 WO2016032737 A1 WO 2016032737A1
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WO
WIPO (PCT)
Prior art keywords
stage
rotors
working fluid
pair
fluid
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/US2015/044529
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English (en)
Inventor
Matthew James FORTINI
William Nicholas Eybergen
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Eaton Corp
Original Assignee
Eaton Corp
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Filing date
Publication date
Application filed by Eaton Corp filed Critical Eaton Corp
Publication of WO2016032737A1 publication Critical patent/WO2016032737A1/fr
Priority to US15/445,458 priority Critical patent/US20170167302A1/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C20/00—Control of, monitoring of, or safety arrangements for, machines or engines
    • F01C20/02—Control of, monitoring of, or safety arrangements for, machines or engines specially adapted for several machines or engines connected in series or in parallel
    • 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
    • F01K7/18—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 turbine being of multiple-inlet-pressure type
    • F01K7/20—Control means specially adapted therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
    • F01C1/14—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F01C1/16—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C11/00—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type
    • F01C11/002—Combinations of two or more machines or engines, each being of rotary-piston or oscillating-piston type of similar working principle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C20/00—Control of, monitoring of, or safety arrangements for, machines or engines
    • F01C20/08—Control of, monitoring of, or safety arrangements for, machines or engines characterised by varying the rotational speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/18—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • 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
    • 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
    • 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
    • F01K7/04—Control means specially adapted therefor
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G5/00—Profiting from waste heat of combustion engines, not otherwise provided for
    • F02G5/02—Profiting from waste heat of exhaust gases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C20/00—Control of, monitoring of, or safety arrangements for, machines or engines
    • F01C20/24—Control of, monitoring of, or safety arrangements for, machines or engines characterised by using valves for controlling pressure or flow rate, e.g. discharge valves
    • F01C20/26—Control of, monitoring of, or safety arrangements for, machines or engines characterised by using valves for controlling pressure or flow rate, e.g. discharge valves using bypass channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/008—Driving elements, brakes, couplings, transmissions specially adapted for rotary or oscillating-piston machines or engines

Definitions

  • This present disclosure relates to volumetric fluid expansion devices that convert waste energy from a power plant to useful work for the purposes of increasing power plant efficiency.
  • Waste heat energy is necessarily produced in many processes that generate energy or convert energy into useful work, such as a power plant. Typically, such waste heat energy is released into the ambient environment. In one application, waste heat energy is generated from an internal combustion engine. Exhaust gases from the engine have a high temperature and pressure and are typically discharged into the ambient environment without any energy recovery process. Alternatively, some approaches have been introduced to recover waste energy and re-use the recovered energy in the same process or in separate processes. However, there is still demand for enhancing the efficiency of energy recovery. SUMMARY
  • a multi-stage volumetric fluid expansion device is provided to generate useful work by expanding a working fluid.
  • the volumetric fluid expansion device can be utilized to recover waste energy from a power plant, such as waste heat energy from a fuel cell or an internal combustion engine.
  • the power plant may be provided in a vehicle or may be provided in a stationary application, such as a generator application.
  • the multi-stage volumetric fluid expansion device may be provided as part of a system for generating mechanical work via a closed-loop Rankine cycle.
  • a system may also include a power plant that produces a waste heat stream, wherein the power plant has a waste heat outlet through which the waste heat stream exits and at least one heat exchanger in fluid communication with the waste heat stream.
  • the heat exchanger heats the working fluid.
  • the multi-stage fluid expansion device can be configured to generate mechanical work at an output device from the working fluid and be provided with a housing within which a first stage, a second stage, and a third stage are disposed.
  • the first, second, and third stages can be configured to sequentially expand the working fluid and product mechanical work at the output device.
  • a condenser may also be provided to partially or fully condense the working fluid while a pump may be provided to pump the condensed working fluid back to the heat exchanger.
  • the volumetric fluid expansion device can be provided with a first working fluid bypass line extending between the first inlet and first outlet of the first fluid expansion stage to allow working fluid to bypass the first stage.
  • the first working fluid bypass line can include a first control valve.
  • the volumetric fluid expansion device can be provided with a second working fluid bypass line extending between the first inlet and first outlet of the second fluid expansion stage to allow working fluid to bypass the first stage.
  • the second working fluid bypass line can include a second control valve.
  • a bypass line to bypass working fluid around the third stage may also be provided.
  • variable speed drive for controlling the rotational speed of the fluid expansion device first, second, and third pairs of rotors may also be provided.
  • the variable speed drive includes a motor connected to the power output device of the fluid expansion device.
  • the multi-stage expansion device first stage may include a first pair of non- contacting rotors disposed between a first inlet and a first outlet while the second stage may include a second pair of non-contacting rotors disposed between a second inlet and a second outlet.
  • the third fluid expansion stage may include a third pair of non-contacting rotors disposed between a third inlet and a third outlet.
  • the power output device is rotated by the first, second, and second third of rotors.
  • the second outlet and third inlet are joined within the housing to form a continuous working fluid passageway extending between the second inlet and the third outlet.
  • the first outlet and the second inlet are joined within the housing to form a continuous working fluid passageway extending between the first inlet and the third outlet.
  • the output device is mechanically coupled to the third stage, the second stage is mechanically coupled to the third stage, and the first stage is mechanically coupled to the second stage such that power developed by each of the first, second, and third stages is transmitted to the power output device.
  • the first pair of rotors has twisted non-contacting lobes, wherein one of the first pair of rotors has a number of twisted lobes that equals a number of twisted lobes of the other of the first pair of rotors.
  • the second and third pairs of rotors may be similarly configured.
  • Figure 1 is a cross-sectional side view of a vehicle having a volumetric fluid expansion device having features that are examples of aspects in accordance with the principles of the present teachings.
  • Figure 2 is a schematic view of a first example of the volumetric fluid expansion device shown in Figure 1.
  • Figure 3 is a perspective view of a rotor suitable for use in the volumetric fluid expansion device shown in Figure 1.
  • Figure 4 is a schematic side view of a stage inlet of the fluid expansion device shown in Figure 1.
  • Figure 5 is a perspective view of an example fluid expansion device having features that are examples of aspects in accordance with the principles of the present disclosure.
  • Figure 6 is a perspective view of the fluid expansion device shown in Figure 5.
  • Figure 7 is a perspective view of the fluid expansion device shown in Figure 5.
  • Figure 8 is a cut-away partial perspective view of the fluid expansion device shown in Figure 5.
  • Figure 9 is a cut-away partial perspective view of the fluid expansion device shown in Figure 5.
  • Figure 10 is a perspective view of the drivetrain of the fluid expansion device shown in Figure 5.
  • a vehicle 10 having wheels 12 for movement along an appropriate surface, such as a roadway.
  • the vehicle 10 includes a power-generation system 14.
  • the system 14 can include a power-plant 16 employing a power-generation cycle.
  • the power-plant 16 can use a specified amount of oxygen, which may be part of a stream of intake air, to generate power.
  • the power-plant 16 can also generate waste heat such in the form of a high-temperature exhaust gas in exhaust line 17 a byproduct of the power-generation cycle.
  • the power-plant 16 can be an internal combustion (IC) engine, such as a spark-ignition or compression-ignition type which combusts a mixture of fuel and air to generate power.
  • the power-plant 16 may be a fuel cell which converts chemical energy from a fuel into electricity through a chemical reaction with oxygen or another oxidizing agent.
  • the vehicle 10 may also include an energy recovery device, for example volumetric fluid expansion device 20, which recovers waste heat from the power-plant 16 to improve the efficiency of the power-plant 16.
  • the volumetric fluid expansion device 20 can be a multi-stage fluid expansion device 20.
  • PCT Patent Cooperation Treaty
  • WO 2014/1 17159 entitled MULTI-STAGE VOLUMETRIC FLUID EXPANSION DEVICE.
  • WO 2014/117159 is hereby incorporated herein by reference in its entirety.
  • an organic Rankine cycle can be used to power the fluid expansion device 20.
  • a piping system 1000 including a heat exchanger 18 can be provided that transfers heat from the exhaust gas line 17 to a working fluid 12 that can then be delivered to the volumetric fluid expansion device 20.
  • the working fluid 12 may be a solvent or combination of solvents, such as ethanol, n-pentane, toluene, and/or water.
  • a condenser 19 can also be provided which creates a low pressure zone for the working fluid 12 and thereby provides a location for the working fluid 12 to condense. Once condensed, the working fluid 12 can be delivered to the heat exchanger 18 via a pump 17.
  • FIG 2 a schematic representation of an example of a multi-stage volumetric fluid expansion device 20 in accordance with the present teachings is shown.
  • Figures 5-10 show a physical example of the volumetric fluid expansion device 20.
  • the multi-stage volumetric fluid expansion device 20 can include a first stage 20-1, a second stage 20-2, and a third stage 20-3. It should be understood that although three stages is shown, the device could be provided with fewer stages, such as two stages, or more stages, such as four, five, six, or more stages.
  • each of the stages 20-1, 20-2, 20-3 is or can be placed in fluid communication with the other such that the working fluid 12 passes sequentially through the stages 20-1, 20-2, 20-3 whereby energy from the fluid is transferred to useful work.
  • the fluid expansion device 20 may also include a power output device 400 configured to transfer useful work from the stages 20-1, 20-2, 20-3 to a power input location of the vehicle 10 or power plant 16.
  • the first stage 20-1 can include a main housing 102 that defines a first working fluid passageway 106 extending between a first inlet 108 and a first outlet 1 10.
  • the second stage 20-2 can include a main housing 202 defining a working fluid passageway 206 extending between a second inlet 208 and a second outlet 210 while the third stage 20-3 can have a main housing 302 defining a working fluid passageway 306 extending between a third inlet 308 and a third outlet 306.
  • the fluid expansion device 20 can also be provided with compartments 150, 152, 154, and 156 to house bearings, timing gears, and/or step gears, as disclosed in PCT Application Publication WO 2014/117159.
  • the compartments 152 and 154 can be configured to provide a boundary between the working fluid pathways 106/206 and 206/306 so as to prevent the working fluid 12 from bypassing internally from the first stage 20-1 to the second stage 20-2 and from the second stage 20-2 to the third stage 20-3 outside of the defined working fluid pathways 106, 206, 306.
  • Disposed within each of the working fluid passageways 106, 206, 306 can be a pair of meshed rotors 130/132, 230/232, and 330/332, respectively.
  • Each pair of meshed rotors 130/132, 230/232, and 330/332 can be configured such that the rotors are overlapping and rotate synchronously in opposite directions.
  • each inlet port 108, 208, 308 can be configured to admit the working fluid 12 at an entering pressure whereas the
  • corresponding outlet port 1 10, 210, 310 can be configured to discharge the working fluid 12 at a leaving pressure lower than the entering pressure.
  • the working fluid 12 enters inlet 108 at a first pressure and leaves outlet 1 10 and enters inlet 208 at a second pressure lower than the first.
  • the working fluid can then exit outlet 210 and enter inlet 308 at a third pressure lower than the second and can subsequently exit outlet 310 at a fourth pressure lower than the third.
  • the pressure drop from the first inlet 108 to the third outlet 310 can be about 10 bar wherein the pressure drop between the first inlet and the first outlet can be about 5 bar, the pressure drop between the second inlet 208 and the second outlet 210 can be about 3 bar, and the pressure drop between the third inlet 308 and the third outlet 310 can be about 2 bar.
  • the housings 102, 202, 302 can be configured such that the first outlet 10 and the second inlet 208 can be formed as a common internal working fluid passageway, as can be the second outlet 210 and the third inlet 208.
  • the working fluid 12 stays entirely internal to the fluid expansion device 20 until reaching the third outlet 310.
  • the volumetric energy recovery device can be provided with one or more bypass lines to allow some or all of the working fluid 12 to bypass one or more of the expander stages 20-1, 20-2, 20-3.
  • Bypassing stages of the expansion device 20 enables the operation of the expansion device 20 to be optimized in light of actual system operating conditions. In one example, bypassing can be effective during transient operating conditions to accommodate the time lag between system activation and the working fluid 12 actually being sufficiently heated (e.g. superheated) in the heat exchanger 18.
  • the bypassing of stages also allows for the same expander 20 to be operated with different working fluids 12.
  • the internal gearing ratios between the stages 20-1, 20-2, 20-3 is a function of the expansion ratio of a particular working fluid to be used in the expander 20.
  • an expander 20 may run optimally for one working fluid, but not another.
  • the internal gearing could be too low resulting in a first stage displacement that is too small for the expansion device 20 to be operated properly.
  • the pressure drop across the first and second expander stages 20-1 and 20-1 could be high enough such that no pressure is available for the third stage 20-3.
  • the third stage 20-3 is designed as the largest displacement size and is responsible for the majority of the power generated by the expansion device 20, such an operating condition would drastically decrease the overall performance of the expansion device 20.
  • the first and/or second stages are bypassed such that it is ensured that the third stage 20-1 receives the working fluid 12 at an optimal pressure, the power output of the third stage 20-3 can be maximized to an extent that much of the otherwise lost power output can be realized at the expander output device 400.
  • a first bypass line 51 can be provided that places the first stage inlet 108 in fluid communication with the first stage outlet 1 10.
  • a second bypass line 53 can be provided that places the second stage inlet 208 (or first stage outlet 1 10) in fluid communication with the second stage outlet 210 (or the third stage inlet 308).
  • a bypass line 55 is provided that places the third stage inlet 308 (or second stage outlet 210) in fluid communication with the third stage outlet 310.
  • first bypass line 51 allows for the working fluid to bypass around the first stage 20-1
  • second bypass line 53 allows for the working fluid to bypass around the second stage 20-2
  • third bypass line 55 allows for the working fluid to bypass around the second stage 20-3.
  • a bypass line connection tube 60 can be provided at the inlet of the second stage 20-2 and that a bypass line connection tube 62 can be provided at the inlet of the third stage 20-3.
  • the bypass line connection tube 60 can be configured to connect to bypass lines 51 and/or 53 via a mechanical connector, for example via a SWAGELOK® type tubing connector.
  • the bypass line connection tube 62 can be configured to connect to bypass line 55 via a mechanical connector, for example via a SWAGELOK® type tubing connector.
  • the bypass line connection tube 60 extends through the second stage housing 202 and into fluid passageway 206 while the bypass line connection tube 62 extends through the third stage housing 302 and into fluid passageway 306.
  • the angle of the bypass line connection tubes 60, 62 with respect to the housing is arranged to optimally introduce the bypassed working fluid 12 into the respective rotors.
  • bypass line 51 can be provided with a control valve 52
  • bypass line 53 can be provided with a control valve 54
  • bypass line 55 can be provided with a control valve 56.
  • valves 52, 54, and 56 are automatically controlled ball-type control valves.
  • the bypass lines and valves do not prevent flow through a particular stage 20-1, 20-2, 20-3, but rather provide a lower pressure drop pathway around the bypassed stage while allowing flow through each stage to be open. Accordingly, when flow is allowed through a bypass line, some of the working fluid 12 will still travel through the expander stage being bypassed although at a much lower volume and pressure drop.
  • the degree to which the working fluid 12 passes through the bypass line instead of the expander stage can be controlled by the valve(s) itself and by the size of the bypass line.
  • the bypass lines and valves can be configured to actively block flow through the stage being bypassed such that all of the working fluid 12 is directed around the stage being bypassed.
  • the bypass valves 52, 54, 56 can be opened and closed (and/or modulated) to bypass any single stage or combination of stages to achieve a desired bypass result.
  • first stage bypass valve 52 is open and the second and third stage bypass valves 54, 56 are closed, at least some of the working fluid 12 will be bypassed around the first stage 20-1, but not bypassed around the second and third stages 20-2, 20-3.
  • first and second bypass valves 52, 54 are open and the third stage bypass valve 56 is closed, at least some of the working fluid 12 will be bypassed around both the first and second stages 20-1, 20-2, but not bypassed around the third stage 20-3.
  • the bypass valves 52, 54, 56 can be further operated to bypass only the second stage 20-2, to bypass only the third stage 20-3, to bypass the second and third stages 20-2, 20-3, and to bypass the first and third stages 20-1, 20-3.
  • the expansion device 20 can also be provided with a variable speed drive 58 to control the rotational speed of the expansion device rotors via an output shaft, for example through the power output device 400.
  • the variable speed drive 58 includes a motor and a controller to vary the speed of the motor.
  • the variable speed drive 58 can be further configured to act as a generator when the power output of the fluid expansion device 20 is sufficient.
  • the variable speed drive 58 can be used to replace the connection between the power output device 400 and the power plant 16 which typically fixes the speed ratio between the power plant 16 crankshaft and the fluid expansion device 20.
  • the utilization of the variable speed drive 58 can decouple the power plant operating speed from the power output device 400 to result in more efficient operation of the fluid expansion device 20.
  • the variable speed drive 58 can be configured and operated to optimize the operation of the fluid expansion device to accommodate different types of working fluids and/or varying operating conditions of the system.
  • the expansion device 20 can be placed in various bypass operational modes.
  • An electronic control system can be provided that monitors, initiates, and controls the initiation of the various modes.
  • an electronic controller 50 monitors various sensors and operating parameters of the expansion device 20 and/or the vehicle power plant 16 to configure the expansion device 20 into the most appropriate bypass mode of operation such that power output of the expansion device 20 is optimized.
  • the electronic controller 50 is schematically shown as including a processor 50A and a non-transient storage medium or memory 50B, such as RAM, flash drive or a hard drive.
  • Memory 50B is for storing executable code, the operating parameters, and potential inputs from an operator interface, while processor 50A is for executing the code.
  • Electronic controller 50 is configured to be connected to a number of inputs and outputs that may be used for implementing the bypass operational modes.
  • the electronic controller 50 can receive information from a vehicle control area network (CAN) bus 56 and information from sensors associated with the expansion device 20 (e.g. mass flow rate sensors, pressure sensors, temperature sensors, etc.).
  • CAN vehicle control area network
  • Examples of outputs from the controller 50 are outputs for the operation of the control valves 52, 54, and 56 and for the operation of the variable speed drive 58. Other outputs are possible as well.
  • the electronic controller 50 is configured to include all required operational outputs for the operation of the fluid expansion device 20.
  • the electronic controller 50 may also include a number of maps or algorithms to correlate the inputs and outputs of the controller 50.
  • the controller 50 may include an algorithm to control the position of the valves 52, 54, and 56 based on the inlet conditions from the ORC system engine speed, and expansion device speed to achieve a desired mass flow rate through the expansion device stages 20-1, 20-2, and 20.
  • the electronic controller 50 may also store a number of predefined and/or configurable parameters and offsets for determining when each of the modes is to be initiated and/or terminated.
  • the term "configurable" refers to a parameter or offset value that can either be selected in the controller (i.e. via a dipswitch) or that can be adjusted within the controller.
  • each of the rotors 130, 132, 230, 232, 330, and 332 can be attached to a respective rotor shaft 138, 140, 238, 240, 338, and 340 (collectively referred to as rotor shafts 38, 40).
  • the rotor shafts 38, 40 can be rigidly connected to the rotors 30, 32 and thus rotate as the rotors are rotated.
  • the rotor shafts 138, 238, 338 can be individual separate shafts rotationally connected through gear sets (e.g. step-up gear sets, step-down gear sets, one-to-one gear sets, etc.) or form part of a common shaft 38.
  • rotor shafts 140, 240, and 340 can be individual separate shafts or form part of a common shaft 38.
  • Each of the rotors 130/132, 230/232, 330/332, collectively referred to as rotors 30, 32 in this section and with reference to Figures 3-4, can provided with a plurality of lobes. As shown in Figure 3, each rotor 30, 32 can be provided with three lobes, 30-1, 30-2, 30-3 in the case of the rotor 30, and 32-1, 32-2, 32-3 in the case of the rotor 32. Although three lobes are shown for each rotor 30 and 32, each of the two rotors may have any number of lobes that is equal to or greater than two.
  • PCT Publication WO 2013/130774 shows a suitable rotor having four lobes. Additionally, the rotors of one or more of the stages 20- 1 , 20-2, 20-3 may have a different number of lobes than the rotors of the other stages 20-1, 20-2, 20-3 in the device 20.
  • the number of lobes can be the same for each rotor 30 and 32. This is in contrast to the construction of typical rotary screw devices and other similarly configured rotating equipment which have a dissimilar number of lobes (e.g. a male rotor with "n" lobes and a female rotor with "n+1" lobes). Furthermore, one of the
  • the rotors 30 and 32 are identical, wherein the rotors 30, 32 are oppositely arranged so that, as viewed from one axial end, the lobes of one rotor are twisted clockwise while the lobes of the meshing rotor are twisted counter-clockwise. Accordingly, when one lobe of the rotor 30, such as the lobe 30-1 is leading with respect to the inlet port 24, a lobe of the rotor 32, such as the lobe 30- 2, is trailing with respect to the inlet port 24, and, therefore with respect to a stream of the high-pressure fluid 12.
  • the first and second rotors 30 and 32 can be interleaved and continuously meshed for unitary rotation with each other.
  • the lobes of each rotor 30, 32 are twisted or helically disposed along the length L of the rotors 30, 32.
  • each rotor 30, 32 has straight lobes along the length L of the rotors 30, 32.
  • the expansion device 20 can be referred to as a "volumetric device" as the sealed or partially sealed fluid volume does not change wherein the working fluid 12 is generally not reduced or compressed.
  • the rotor shafts 38, 40 can be rotated by the working fluid 12 as the fluid undergoes expansion from the higher first pressure working fluid 12 to the lower second pressure working fluid 12. Accordingly, the shafts 38, 40 are configured to capture the work or power generated by the expansion device 20 during the expansion of the fluid 12 that takes place between the inlet port 108, 208, 308 and the respective outlet port 110, 210, 310. As discussed previously, the work is transferred from the shafts 38, 40 as output torque from the expansion device 20 via output device 400.
  • each of the rotor lobes 30-1 to 30-3 and 32-1 to 32-3 has a lobe geometry in which the twist of each of the first and second rotors 30 and 32 is constant along their substantially matching length L.
  • the lobes 130, 132, 230, 232, 330, 332 can be provided without a twist although a drop in efficiency would be expected to occur.
  • lobes 130, 132 are provided as straight lobes while lobes 230, 232, 330, 332 are provided as twisted lobes.
  • the length L of all rotors 130, 132, 230, 232, 330, 332 is the same.
  • the length L of the rotors 130, 132 is less than a length L of the rotors 230, 232, which is in turn less than a Length L of the rotors 330, 332.

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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)

Abstract

La présente invention porte sur un dispositif de détente multi-étages ayant des capacités de dérivation et un entraînement à vitesse variable. Dans un exemple, le dispositif de détente multi-étages comporte un boîtier à l'intérieur duquel se situent un premier étage, un deuxième étage et un troisième étage. Le boîtier peut également être conçu avec des conduits internes de fluide de travail destinés à diriger un fluide de travail du premier étage vers le deuxième étage et/ou du deuxième étage vers le troisième étage. Tous les étages peuvent comprendre deux rotors sans contact qui sont en prise mécanique l'un avec l'autre et avec un dispositif de sortie de puissance, de sorte que l'énergie extraite du fluide de travail est convertie en travail mécanique au niveau du dispositif de sortie. Dans un exemple, une ligne de dérivation est prévue pour dévier le fluide de travail au niveau du premier étage et une ligne de dérivation est prévue pour dévier le fluide de travail au niveau du deuxième étage.
PCT/US2015/044529 2014-08-28 2015-08-10 Stratégie d'efficacité optimisée pour un détendeur volumétrique multi-étages Ceased WO2016032737A1 (fr)

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US62/043,082 2014-08-28

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US10465518B2 (en) 2016-05-09 2019-11-05 Sunnyco Inc. Pneumatic engine and related methods
US10641239B2 (en) 2016-05-09 2020-05-05 Sunnyco Inc. Pneumatic engine and related methods

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US20100192574A1 (en) * 2006-01-19 2010-08-05 Langson Richard K Power compounder
JP2013096322A (ja) * 2011-11-02 2013-05-20 Toyota Industries Corp 廃熱回生システム
JP2013119831A (ja) * 2011-12-08 2013-06-17 Toyota Industries Corp 動力回収装置
WO2014117159A1 (fr) * 2013-01-28 2014-07-31 Eaton Corporation Dispositif de détente de fluide volumétrique à plusieurs étages

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EP1998013A2 (fr) * 2007-04-16 2008-12-03 Turboden S.r.l. Appareil pour la production d'énergie électrique à l'aide de fumées à haute température
JP2013096322A (ja) * 2011-11-02 2013-05-20 Toyota Industries Corp 廃熱回生システム
JP2013119831A (ja) * 2011-12-08 2013-06-17 Toyota Industries Corp 動力回収装置
WO2014117159A1 (fr) * 2013-01-28 2014-07-31 Eaton Corporation Dispositif de détente de fluide volumétrique à plusieurs étages

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10465518B2 (en) 2016-05-09 2019-11-05 Sunnyco Inc. Pneumatic engine and related methods
US10641239B2 (en) 2016-05-09 2020-05-05 Sunnyco Inc. Pneumatic engine and related methods

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