CA2394819A1 - Combined pump generator and turbine - Google Patents
Combined pump generator and turbine Download PDFInfo
- Publication number
- CA2394819A1 CA2394819A1 CA 2394819 CA2394819A CA2394819A1 CA 2394819 A1 CA2394819 A1 CA 2394819A1 CA 2394819 CA2394819 CA 2394819 CA 2394819 A CA2394819 A CA 2394819A CA 2394819 A1 CA2394819 A1 CA 2394819A1
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- Canada
- Prior art keywords
- working fluid
- turbine
- pump
- common shaft
- impeller
- 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.)
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/04—Shafts or bearings, or assemblies thereof
- F04D29/046—Bearings
- F04D29/047—Bearings hydrostatic; hydrodynamic
-
- 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
- F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
- F01D15/08—Adaptations for driving, or combinations with, pumps
-
- 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
- F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
- F01D15/10—Adaptations for driving, or combinations with, electric generators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D13/00—Pumping installations or systems
- F04D13/02—Units comprising pumps and their driving means
- F04D13/04—Units comprising pumps and their driving means the pump being fluid driven
- F04D13/043—Units comprising pumps and their driving means the pump being fluid driven the pump wheel carrying the fluid driving means
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E20/00—Combustion technologies with mitigation potential
- Y02E20/16—Combined cycle power plant [CCPP], or combined cycle gas turbine [CCGT]
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
Abstract
This invention combines the functions of a pump, a turbine and a generator interconnected on a common shaft. The casing components are separably connected to form an enclosure such that only static seals are required to prevent working fluid from leaking. A portion of the working fluid can be used in the hydrodynamic action of the radial bearings and the thrust bearings. A portion of the working fluid can be used to cool the generator rotor. A coolant impeller can be rigidly attached to the common shaft to enhance flow of the portion of working fluid used for hydrodynamic bearing support and rotor cooling. Multiple pump impellers can be rigidly attached in series on the common shaft.
Multiple turbine impellers can be rigidly attached in series on the common shaft.
Multiple turbine impellers can be rigidly attached in series on the common shaft.
Description
COMBINED PUMP, GENERATOR AND TURBINE
DESCRIPTION OF EXISTING TECHNOLOGY
A common power cycle used to generate electricity is the Rankine Cycle. The Rankine cycle operates by compressing a fluid in its liquid state, vaporizing and superheating said fluid, expanding said fluid in its vapour state through a device to extract energy and condensing said fluid. The energy input to the cycle causes said fluid to vaporize and superheat. The energy rejection from the cycle causes said fluid to condense.
to The most typical working fluid used in Rankine cycles is water-steam. The traditional steam power plant is based on any of a variety of fuels including nuclear, coal, oil, wood, etc. and, along with hydroelectric installations, has been the backbone of the electrical power-grid of North America.
Working fluids such as butane, pentane and ammonia have been used in applied Rankine cycles for 15 special systems such as geothermal and ocean energy conversion. These special systems are "closed"
recirculating designs where leakage is highly undesirable.
Application of a Rankine cycle will typically use a pump to compress a working fluid liquid and a turbine to expand a working fluid vapour. A generator or alternator is often attached to the shaft of a 2o turbine used to expand a working fluid and extract power in an applied Rankine cycle. It is not unusual for a generator or alternator to be attached to the shaft of a turbine through a gearbox to match the equipment speeds.
A recent development has been high-speed alternators that can be attached directly to a turbine shaft 25 and operate at the normal operating speed of the turbine. Typically these high-speed alternators use a rotor formed by permanent magnets attached to the rotating shaft and secured to withstand the stresses produced by the high rotation speeds. A stationary coil structure encloses the rotor without contact. A
rotating magnetic field of the rotor induces a current in the coil and the assemblage extracts energy in the form of electricity. Electricity produced is passed through conditioning circuitry that modifies the 30 voltage, amperage, frequency and phase to match the desired final result.
The term alternator refers to the specific type of generator that produces an alternating current.
DESCRIPTION OF THE NEED
35 Traditional systems, based on a water-steam Rankine cycle, are generally considered "open" systems.
Water-steam Rankine cycle systems are designed to account for steam uses outside the Rankine cycle such as sootblowers and unrelated process use. They include water blowdown to remove impurities and they are known to leak steam to the atmosphere through poorly maintained seals.
4o Systems that use working fluids other than water-steam are usually designed to be "closed" systems.
Alternate choices of working fluid are usually expensive to replenish and are often a safety or environmental hazard. Thus it is important that said "closed" systems be designed not to leak and must be well maintained to prevent wear-related deterioration. Dynamic seals between the working fluid and the environment are the most susceptible to leakage. The present invention is a design that 45 eliminates the problem of dynamic seals that can allow leakage of working fluid to the environment.
DESCRIPTION OF THE DRAWINGS
Fig. 1 is a semi-diagrammatic view of a combined pump-generator-turbine according to a single coil 5o structure embodiment of the invention showing a centerline cut-away cross-section;
Fig. 2 depicts the same view as Fig. 1 with the components separated;
Fig. 3 is a semi-diagrammatic view of a combined pump-generator-turbine according to a double coil 55 structure embodiment of the invention showing a centerline cut-away cross-section;
Fig. 4 depicts the same view as Fig. 3 with the components separated;
Fig. 5 is an embodiment of the invention as depicted in Fig. 1 using a horizontal split casing with an 6o added coolant impeller;
Fig. 6 depicts the same view as Fig. 5 with the casing segregated from the internal components;
Fig. 7 is a partial semi-diagrammatic view of the pump section of Fig. S
depicting a two-stage pump;
65 and, Fig. 8 is a partial semi-diagrammatic view of the turbine section of Fig. S
depicting a two-stage turbine.
7o DESCRIPTION OF THE INVENTION
Fig. 1 and Fig. 2 depict power unit 1 that combines the functions of fluid pump section 4, fluid turbine section 3 and electrical generator section 5. A working fluid enters inlet nozzle 43 and is directed through inlet channel 45 to pump impeller 42. Pump impeller 42 is rigidly attached to shaft 10; shaft 75 10 being constrained to effectively allow only rotational movement. Said working fluid is pressurized by rotational action of pump impeller 42 and directed through exhaust channel 46 to exit outlet nozzle 44. Upon leaving power unit 1, said working fluid is treated to input energy into said working fluid before returning to power unit 1. Said working fluid with said additional energy content enters inlet nozzle 33, passes through distribution channel 35 and is directed by inlet vanes 37 to turbine impeller so 32. Turbine impeller 32 is rigidly attached to shaft 10. Said working fluid expands through turbine impeller 32 imparting said rotational action to shaft 10. Said working fluid leaves turbine impeller 32 through exhaust channel 36 and exits power unit 1 through outlet nozzle 34.
Rigidly attached to shaft is rotor 6 consisting of source 61 of magnetic fields that serve to produce rotating magnetic fields by said rotational action of shaft 10. Source 61 of magnetic fields creates coherent magnetic fields 85 external to shaft 10. Coil structure 52 encompasses but does not contact rotor 6 such that said rotating magnetic fields intersect conducting loops of coil structure 52, inducing a current flow within coil structure 52 when shaft 10 rotates. Electrical power is extracted from coil structure 52 through electrical outlet leads 54 that form the ends of coil structure 52. Coil seal 53 prevents said working fluid from contacting coil structure 52. Rotor 6 is most commonly formed by permanent magnets 9o acting as source 61 of magnetic fields held in place by containment 62.
Containment 62 can be a high-strength composite winding immovably holding source 61 of magnetic fields in the form of permanent magnets to shaft 10 to form rotor 6.
Shaft 10 is supported for rotational motion by radial support bearing 11 and radial support bearing 13 95 and for lateral motion by thrust bearing 14. It is an aspect of this invention that radial support bearing 11, radial support bearing 13 and thrust bearing 14 are hydrodynamic bearings using said working fluid for bearing support. A portion of said working fluid at high pressure leaving outlet nozzle 44 is diverted through takeoff 16 and fed into bearing lubrication feeds 17. Said portion of said working fluid passes through bearing lubrication feeds 17 into bearing lubrication passages 18 to be used by 100 bearing 11, bearing 13 and bearing 14. Said portion of said working fluid leaves bearing 1 l, bearing 13 and bearing 14 and is collected in return 19. Upon leaving power unit 1 through return 19 said portion of said working fluid is combined with said working fluid leaving turbine section 3 at lower pressure through outlet nozzle 34. Said portion of said working fluid leaving bearing 11 must travel next to shaft 10 through the gap formed by rotor 6 and coil structure 52 wherein said portion of said 105 working fluid leaving bearing 11 absorbs heat and cools rotor 6 and coil structure 52. It is an aspect of this invention that said working fluid is used to cool rotor 6 and coil structure 52. It is readily apparent that said portion of said working fluid can alternately be supplied by a separate pump not shown.
Energy extracted from said working fluid by turbine impeller 32 is imparted to shaft 10 in the form of 110 rotational motion. The energy used by pump impeller 42 to pressurize said working fluid is less than said energy extracted by turbine impeller 32. Some energy is absorbed by said portion of said working fluid while passing through bearing 11, bearing 13 and bearing 14 and while passing between rotor 6 and coil structure 52. The balance of said energy extracted from said working fluid by turbine impeller 32 is extracted by coil structure 52 as electricity.
When operated in a Rankine cycle, power unit 1 pressurizes said working fluid as a liquid in pump section 4 and expands said working fluid as a vapour in turbine section 3. A
large dii~erence exists between said energy extracted from said working fluid by turbine impeller 32 and said energy used by pump impeller 42 to pressurize said working fluid. Energy of said large difference is available to be t20 converted into electricity in generator section 5.
Power unit 1 depicts generator section 5 with casing 51 forming the centre section. It is noted that casing 41 of pump section 4 is separably connected to casing 51 of generator section 5 such that only a static seal is required to prevent said working fluid from leaking. It is noted that casing 31 of turbine 125 section 3 is separably connected to casing 51 of generator section 5 such that only a static seal is required to prevent said working fluid from leaking. Turbine section casing 31, generator section casing 51 and pump section casing 41 form the casing enclosure for power unit 1. It is noted that nozzle 33, nozzle 34, nozzle 43 and nozzle 44 can be separably connected to external piping such that only static seals are required to prevent said working fluid from leaking. It is noted that takeoff 16, 130 feed 17 and return 19 can be reparably connected to external piping such that only static seals are required to prevent said working fluid from leaking. It is readily apparent that the fluid path from takeoff 16 to feed 17 could be incorporated within casing 41 and casing 51 such that no external connection is required. It is readily apparent that the fluid path from return 19 to exhaust channel 36 could be incorporated within casing 51 and casing 31 such that no external connection is required.
Fig. 3 and Fig. 4 depict power unit 2 that is similar to power unit 1 with the exception that coil structure 52 and rotor 6 have been segregated into two sections separated by bearing support 7. The function of turbine section 3, pump section 4 and generator section 5 are unchanged from those of power unit 1. Radial support bearing 12 is mounted on shaft 10 and located by bearing support 7. Said 140 portion of said working fluid is diverted through takeoff 16 and fed into bearing lubrication feeds 17.
Said portion of said working fluid passes through bearing lubrication feeds 17 into bearing lubrication passages 18 to be used by bearing 11, bearing 12, bearing 13 and bearing 14.
Said portion of said working fluid leaves bearing 11, bearing 12, bearing 13 and bearing 14 and is collected in returns 19.
Said portion of said fluid passing through bearing 12 must travel next to shaft 10 between the gap 145 formed by rotor 6 and coil structure 52 with some of said working fluid travelling towards pump section 4 and some of said working fluid travelling towards turbine section 3.
It is an aspect of this invention that the cooling effect of said portion of said working fluid is enhanced by a balance flow in opposing directions of said working fluid. It is readily apparent that generator section 5 may be segregated into any number of separate sections.
Fig. 5 and Fig. 6 depict power unit 9 that is similar to power unit 1 with the exception that pump casing 41, generator casing 51 and turbine casing 31 have been combined laterally and split horizontally to form upper casing 91 and lower casing 92. Casing 91 and casing 92 are reparably connected to form a casing enclosure for power unit 9 such that only a static seal is required to prevent said working fluid 155 from leaking. A horizontal split casing design is often more useful for manufacture. Coolant impeller 8 is shown as part of power unit 9. Coolant impeller 8 enhances flow of said portion of said working fluid used by bearing 11, bearing 13 and bearing 14 and used for cooling rotor 6 and coil structure 52 by performing a pumping action on said portion of said working fluid. The outlet of coolant impeller 8 feeds directly to return 19. Coolant impeller 8 may be used if there is insufficient pressure differential 16o between said working fluid leaving pump section 4 and said working fluid leaving turbine section 3.
It may be noted that there exists a turbine bypass path for said working fluid allowing said working fluid to bypass turbine impeller 32 by flowing from distribution channel 35 to the gap between thrust bearing 14 and turbine impeller 32 and into return 19. Flow through said turbine bypass path is 165 minimized by close gap tolerance between turbine impeller 32 and turbine casing 31. Said flow through said turbine bypass path is further limited as said portion of said working fluid passing through thrust bearing 14 to the gap between thrust bearing 14 and turbine impeller 32 is similar in pressure to said working fluid in distribution channel 35. It is an aspect of this invention that an effective dynamic seal of turbine impeller 32 is formed by the arrangement of the flow path of said portion of said 17o working fluid passing through bearing 13 and thrust bearing 14. It is readily apparent that a conventional dynamic seal could be added to further limit flow of said working fluid through said turbine bypass path.
It may be noted that there exists a pump bypass path for said working fluid allowing said working fluid 175 to bypass pump impeller 42 by flowing from exhaust channel 46 to the gap between generator casing 51 and pump impeller 42. Flow through said pump bypass path is minimized by close gap tolerance between pump impeller 42 and pump casing 41. Said flow through said pump bypass path is further limited as said portion of said working fluid passing through bearing 11 to the gap between pump casing 4land pump impeller 42 is similar in pressure to said working fluid in exhaust channel 46. It is 18o an aspect of this invention that an effective dynamic seal of pump impeller 42 is formed by the arrangement of the flow path of said portion of said working fluid passing through bearing 11. It is readily apparent that a conventional dynamic seal could be added to further limit flow of said working fluid through said pump bypass path.
185 Power unit l, power unit 2 and power unit 9 each depict a single stage turbine and a single stage pump.
Fig. 7 depicts pump section 4 of power unit 9 wherein two pump impellers 42 are mounted in series on common shaft 10 with connecting channel 48 in casing 91 and casing 92. Said working fluid enters inlet nozzle 43, passes through each impeller 42 in sequence and leaves pump section 4 through outlet nozzle 44. It is readily apparent that the present invention may include multiple pump impellers 42 19o commonly mounted on shaft 10 and attached in series wherein the output of each pump impeller 42 feeds the input of the next pump impeller 42 through connecting channels 48 until the final pump impeller 42 feeds exhaust channel 46.
Fig. 8 depicts turbine section 3 of power unit 9 wherein two turbine impellers 32 are mounted in series 195 on common shaft 10 with connecting channel 38 in casing 91 and casing 92.
Said working fluid enters inlet nozzle 33, passes through each impeller 32 in sequence and leaves turbine section 3 through outlet nozzle 34. It is readily apparent that the present invention may include multiple turbine impellers 32 commonly mounted on shaft 10 and attached in series wherein the output of each turbine impeller 32 feeds the input of the next turbine impeller 32 through connecting channels 38 until the 20o final turbine impeller 32 feeds exhaust channel 36.
DESCRIPTION OF EXISTING TECHNOLOGY
A common power cycle used to generate electricity is the Rankine Cycle. The Rankine cycle operates by compressing a fluid in its liquid state, vaporizing and superheating said fluid, expanding said fluid in its vapour state through a device to extract energy and condensing said fluid. The energy input to the cycle causes said fluid to vaporize and superheat. The energy rejection from the cycle causes said fluid to condense.
to The most typical working fluid used in Rankine cycles is water-steam. The traditional steam power plant is based on any of a variety of fuels including nuclear, coal, oil, wood, etc. and, along with hydroelectric installations, has been the backbone of the electrical power-grid of North America.
Working fluids such as butane, pentane and ammonia have been used in applied Rankine cycles for 15 special systems such as geothermal and ocean energy conversion. These special systems are "closed"
recirculating designs where leakage is highly undesirable.
Application of a Rankine cycle will typically use a pump to compress a working fluid liquid and a turbine to expand a working fluid vapour. A generator or alternator is often attached to the shaft of a 2o turbine used to expand a working fluid and extract power in an applied Rankine cycle. It is not unusual for a generator or alternator to be attached to the shaft of a turbine through a gearbox to match the equipment speeds.
A recent development has been high-speed alternators that can be attached directly to a turbine shaft 25 and operate at the normal operating speed of the turbine. Typically these high-speed alternators use a rotor formed by permanent magnets attached to the rotating shaft and secured to withstand the stresses produced by the high rotation speeds. A stationary coil structure encloses the rotor without contact. A
rotating magnetic field of the rotor induces a current in the coil and the assemblage extracts energy in the form of electricity. Electricity produced is passed through conditioning circuitry that modifies the 30 voltage, amperage, frequency and phase to match the desired final result.
The term alternator refers to the specific type of generator that produces an alternating current.
DESCRIPTION OF THE NEED
35 Traditional systems, based on a water-steam Rankine cycle, are generally considered "open" systems.
Water-steam Rankine cycle systems are designed to account for steam uses outside the Rankine cycle such as sootblowers and unrelated process use. They include water blowdown to remove impurities and they are known to leak steam to the atmosphere through poorly maintained seals.
4o Systems that use working fluids other than water-steam are usually designed to be "closed" systems.
Alternate choices of working fluid are usually expensive to replenish and are often a safety or environmental hazard. Thus it is important that said "closed" systems be designed not to leak and must be well maintained to prevent wear-related deterioration. Dynamic seals between the working fluid and the environment are the most susceptible to leakage. The present invention is a design that 45 eliminates the problem of dynamic seals that can allow leakage of working fluid to the environment.
DESCRIPTION OF THE DRAWINGS
Fig. 1 is a semi-diagrammatic view of a combined pump-generator-turbine according to a single coil 5o structure embodiment of the invention showing a centerline cut-away cross-section;
Fig. 2 depicts the same view as Fig. 1 with the components separated;
Fig. 3 is a semi-diagrammatic view of a combined pump-generator-turbine according to a double coil 55 structure embodiment of the invention showing a centerline cut-away cross-section;
Fig. 4 depicts the same view as Fig. 3 with the components separated;
Fig. 5 is an embodiment of the invention as depicted in Fig. 1 using a horizontal split casing with an 6o added coolant impeller;
Fig. 6 depicts the same view as Fig. 5 with the casing segregated from the internal components;
Fig. 7 is a partial semi-diagrammatic view of the pump section of Fig. S
depicting a two-stage pump;
65 and, Fig. 8 is a partial semi-diagrammatic view of the turbine section of Fig. S
depicting a two-stage turbine.
7o DESCRIPTION OF THE INVENTION
Fig. 1 and Fig. 2 depict power unit 1 that combines the functions of fluid pump section 4, fluid turbine section 3 and electrical generator section 5. A working fluid enters inlet nozzle 43 and is directed through inlet channel 45 to pump impeller 42. Pump impeller 42 is rigidly attached to shaft 10; shaft 75 10 being constrained to effectively allow only rotational movement. Said working fluid is pressurized by rotational action of pump impeller 42 and directed through exhaust channel 46 to exit outlet nozzle 44. Upon leaving power unit 1, said working fluid is treated to input energy into said working fluid before returning to power unit 1. Said working fluid with said additional energy content enters inlet nozzle 33, passes through distribution channel 35 and is directed by inlet vanes 37 to turbine impeller so 32. Turbine impeller 32 is rigidly attached to shaft 10. Said working fluid expands through turbine impeller 32 imparting said rotational action to shaft 10. Said working fluid leaves turbine impeller 32 through exhaust channel 36 and exits power unit 1 through outlet nozzle 34.
Rigidly attached to shaft is rotor 6 consisting of source 61 of magnetic fields that serve to produce rotating magnetic fields by said rotational action of shaft 10. Source 61 of magnetic fields creates coherent magnetic fields 85 external to shaft 10. Coil structure 52 encompasses but does not contact rotor 6 such that said rotating magnetic fields intersect conducting loops of coil structure 52, inducing a current flow within coil structure 52 when shaft 10 rotates. Electrical power is extracted from coil structure 52 through electrical outlet leads 54 that form the ends of coil structure 52. Coil seal 53 prevents said working fluid from contacting coil structure 52. Rotor 6 is most commonly formed by permanent magnets 9o acting as source 61 of magnetic fields held in place by containment 62.
Containment 62 can be a high-strength composite winding immovably holding source 61 of magnetic fields in the form of permanent magnets to shaft 10 to form rotor 6.
Shaft 10 is supported for rotational motion by radial support bearing 11 and radial support bearing 13 95 and for lateral motion by thrust bearing 14. It is an aspect of this invention that radial support bearing 11, radial support bearing 13 and thrust bearing 14 are hydrodynamic bearings using said working fluid for bearing support. A portion of said working fluid at high pressure leaving outlet nozzle 44 is diverted through takeoff 16 and fed into bearing lubrication feeds 17. Said portion of said working fluid passes through bearing lubrication feeds 17 into bearing lubrication passages 18 to be used by 100 bearing 11, bearing 13 and bearing 14. Said portion of said working fluid leaves bearing 1 l, bearing 13 and bearing 14 and is collected in return 19. Upon leaving power unit 1 through return 19 said portion of said working fluid is combined with said working fluid leaving turbine section 3 at lower pressure through outlet nozzle 34. Said portion of said working fluid leaving bearing 11 must travel next to shaft 10 through the gap formed by rotor 6 and coil structure 52 wherein said portion of said 105 working fluid leaving bearing 11 absorbs heat and cools rotor 6 and coil structure 52. It is an aspect of this invention that said working fluid is used to cool rotor 6 and coil structure 52. It is readily apparent that said portion of said working fluid can alternately be supplied by a separate pump not shown.
Energy extracted from said working fluid by turbine impeller 32 is imparted to shaft 10 in the form of 110 rotational motion. The energy used by pump impeller 42 to pressurize said working fluid is less than said energy extracted by turbine impeller 32. Some energy is absorbed by said portion of said working fluid while passing through bearing 11, bearing 13 and bearing 14 and while passing between rotor 6 and coil structure 52. The balance of said energy extracted from said working fluid by turbine impeller 32 is extracted by coil structure 52 as electricity.
When operated in a Rankine cycle, power unit 1 pressurizes said working fluid as a liquid in pump section 4 and expands said working fluid as a vapour in turbine section 3. A
large dii~erence exists between said energy extracted from said working fluid by turbine impeller 32 and said energy used by pump impeller 42 to pressurize said working fluid. Energy of said large difference is available to be t20 converted into electricity in generator section 5.
Power unit 1 depicts generator section 5 with casing 51 forming the centre section. It is noted that casing 41 of pump section 4 is separably connected to casing 51 of generator section 5 such that only a static seal is required to prevent said working fluid from leaking. It is noted that casing 31 of turbine 125 section 3 is separably connected to casing 51 of generator section 5 such that only a static seal is required to prevent said working fluid from leaking. Turbine section casing 31, generator section casing 51 and pump section casing 41 form the casing enclosure for power unit 1. It is noted that nozzle 33, nozzle 34, nozzle 43 and nozzle 44 can be separably connected to external piping such that only static seals are required to prevent said working fluid from leaking. It is noted that takeoff 16, 130 feed 17 and return 19 can be reparably connected to external piping such that only static seals are required to prevent said working fluid from leaking. It is readily apparent that the fluid path from takeoff 16 to feed 17 could be incorporated within casing 41 and casing 51 such that no external connection is required. It is readily apparent that the fluid path from return 19 to exhaust channel 36 could be incorporated within casing 51 and casing 31 such that no external connection is required.
Fig. 3 and Fig. 4 depict power unit 2 that is similar to power unit 1 with the exception that coil structure 52 and rotor 6 have been segregated into two sections separated by bearing support 7. The function of turbine section 3, pump section 4 and generator section 5 are unchanged from those of power unit 1. Radial support bearing 12 is mounted on shaft 10 and located by bearing support 7. Said 140 portion of said working fluid is diverted through takeoff 16 and fed into bearing lubrication feeds 17.
Said portion of said working fluid passes through bearing lubrication feeds 17 into bearing lubrication passages 18 to be used by bearing 11, bearing 12, bearing 13 and bearing 14.
Said portion of said working fluid leaves bearing 11, bearing 12, bearing 13 and bearing 14 and is collected in returns 19.
Said portion of said fluid passing through bearing 12 must travel next to shaft 10 between the gap 145 formed by rotor 6 and coil structure 52 with some of said working fluid travelling towards pump section 4 and some of said working fluid travelling towards turbine section 3.
It is an aspect of this invention that the cooling effect of said portion of said working fluid is enhanced by a balance flow in opposing directions of said working fluid. It is readily apparent that generator section 5 may be segregated into any number of separate sections.
Fig. 5 and Fig. 6 depict power unit 9 that is similar to power unit 1 with the exception that pump casing 41, generator casing 51 and turbine casing 31 have been combined laterally and split horizontally to form upper casing 91 and lower casing 92. Casing 91 and casing 92 are reparably connected to form a casing enclosure for power unit 9 such that only a static seal is required to prevent said working fluid 155 from leaking. A horizontal split casing design is often more useful for manufacture. Coolant impeller 8 is shown as part of power unit 9. Coolant impeller 8 enhances flow of said portion of said working fluid used by bearing 11, bearing 13 and bearing 14 and used for cooling rotor 6 and coil structure 52 by performing a pumping action on said portion of said working fluid. The outlet of coolant impeller 8 feeds directly to return 19. Coolant impeller 8 may be used if there is insufficient pressure differential 16o between said working fluid leaving pump section 4 and said working fluid leaving turbine section 3.
It may be noted that there exists a turbine bypass path for said working fluid allowing said working fluid to bypass turbine impeller 32 by flowing from distribution channel 35 to the gap between thrust bearing 14 and turbine impeller 32 and into return 19. Flow through said turbine bypass path is 165 minimized by close gap tolerance between turbine impeller 32 and turbine casing 31. Said flow through said turbine bypass path is further limited as said portion of said working fluid passing through thrust bearing 14 to the gap between thrust bearing 14 and turbine impeller 32 is similar in pressure to said working fluid in distribution channel 35. It is an aspect of this invention that an effective dynamic seal of turbine impeller 32 is formed by the arrangement of the flow path of said portion of said 17o working fluid passing through bearing 13 and thrust bearing 14. It is readily apparent that a conventional dynamic seal could be added to further limit flow of said working fluid through said turbine bypass path.
It may be noted that there exists a pump bypass path for said working fluid allowing said working fluid 175 to bypass pump impeller 42 by flowing from exhaust channel 46 to the gap between generator casing 51 and pump impeller 42. Flow through said pump bypass path is minimized by close gap tolerance between pump impeller 42 and pump casing 41. Said flow through said pump bypass path is further limited as said portion of said working fluid passing through bearing 11 to the gap between pump casing 4land pump impeller 42 is similar in pressure to said working fluid in exhaust channel 46. It is 18o an aspect of this invention that an effective dynamic seal of pump impeller 42 is formed by the arrangement of the flow path of said portion of said working fluid passing through bearing 11. It is readily apparent that a conventional dynamic seal could be added to further limit flow of said working fluid through said pump bypass path.
185 Power unit l, power unit 2 and power unit 9 each depict a single stage turbine and a single stage pump.
Fig. 7 depicts pump section 4 of power unit 9 wherein two pump impellers 42 are mounted in series on common shaft 10 with connecting channel 48 in casing 91 and casing 92. Said working fluid enters inlet nozzle 43, passes through each impeller 42 in sequence and leaves pump section 4 through outlet nozzle 44. It is readily apparent that the present invention may include multiple pump impellers 42 19o commonly mounted on shaft 10 and attached in series wherein the output of each pump impeller 42 feeds the input of the next pump impeller 42 through connecting channels 48 until the final pump impeller 42 feeds exhaust channel 46.
Fig. 8 depicts turbine section 3 of power unit 9 wherein two turbine impellers 32 are mounted in series 195 on common shaft 10 with connecting channel 38 in casing 91 and casing 92.
Said working fluid enters inlet nozzle 33, passes through each impeller 32 in sequence and leaves turbine section 3 through outlet nozzle 34. It is readily apparent that the present invention may include multiple turbine impellers 32 commonly mounted on shaft 10 and attached in series wherein the output of each turbine impeller 32 feeds the input of the next turbine impeller 32 through connecting channels 38 until the 20o final turbine impeller 32 feeds exhaust channel 36.
Claims (10)
1. A combination of equipment to extract energy from a working fluid and which comprises of:
a casing enclosure consisting of two or more casing components separably connected using static seals, a common shaft, a turbine section consisting of a turbine impeller rigidly attached to the common shaft, inlet vanes directing the working fluid into the turbine impeller, a turbine distribution channel, and a turbine exhaust channel, a pump section consisting of a pump impeller rigidly attached to the common shaft, a pump inlet channel, and a pump exhaust channel, one or more rotors, each consisting of a source of magnetic fields rigidly attached to the common shaft, a coil structure encompassing each rotor such that the magnetic fields of that rotor intersect conducting loops of the coil structure, two or more radial support bearings supporting the common shaft and allowing rotation of the common shaft, and one or more thrust bearings maintaining lateral position of the common shaft.
a casing enclosure consisting of two or more casing components separably connected using static seals, a common shaft, a turbine section consisting of a turbine impeller rigidly attached to the common shaft, inlet vanes directing the working fluid into the turbine impeller, a turbine distribution channel, and a turbine exhaust channel, a pump section consisting of a pump impeller rigidly attached to the common shaft, a pump inlet channel, and a pump exhaust channel, one or more rotors, each consisting of a source of magnetic fields rigidly attached to the common shaft, a coil structure encompassing each rotor such that the magnetic fields of that rotor intersect conducting loops of the coil structure, two or more radial support bearings supporting the common shaft and allowing rotation of the common shaft, and one or more thrust bearings maintaining lateral position of the common shaft.
2. The combination defined in claim 1, wherein a portion of the working fluid is directed to the two or more radial support bearings and to the one or more thrust bearings to be used for hydrodynamic support.
3. The combination defined in claim 1, wherein a portion of the working fluid is directed through a gap between the one or more rotors and the encompassing coil structures to cool the rotor.
4. The combination defined in claim 2, wherein a coolant impeller is rigidly attached to the common shaft to enhance flow of the portion of working fluid used for hydrodynamic support of the bearings.
5. The combination defined in claim 3, wherein a coolant impeller is rigidly attached to the common shaft to enhance flow of the portion of working fluid directed through a gap between one or more rotors and the encompassing coil structures to cool the rotor.
6. The combination defined in claim 1, wherein:
the turbine section consists of:
one or more turbine impellers rigidly attached to the common shaft, inlet vanes directing the working fluid into each turbine impeller, a turbine distribution channel preceding the first turbine impeller, turbine connecting channels between turbine impellers, a turbine exhaust channel following the last turbine impeller, and the pump section consists of:
one or more pump impellers rigidly attached to the common shaft, a pump inlet channel preceding the first pump impeller, pump connecting channels between pump impellers, a pump exhaust channel following the last pump impeller.
the turbine section consists of:
one or more turbine impellers rigidly attached to the common shaft, inlet vanes directing the working fluid into each turbine impeller, a turbine distribution channel preceding the first turbine impeller, turbine connecting channels between turbine impellers, a turbine exhaust channel following the last turbine impeller, and the pump section consists of:
one or more pump impellers rigidly attached to the common shaft, a pump inlet channel preceding the first pump impeller, pump connecting channels between pump impellers, a pump exhaust channel following the last pump impeller.
7. The combination defined in claim 6, wherein a portion of the working fluid is directed to the two or more radial support bearings and to the one or more thrust bearings to be used for hydrodynamic support.
8. The combination defined in claim 6, wherein a portion of the working fluid is directed through a gap between the one or more rotors and the encompassing coil structures to cool the rotor.
9. The combination defined in claim 7, wherein a coolant impeller is rigidly attached to the common shaft to enhance flow of the portion of working fluid used for hydrodynamic support of the bearings.
10. The combination defined in claim 8, wherein a coolant impeller is rigidly attached to the common shaft to enhance flow of the portion of working fluid directed through a gap between one or more rotors and the encompassing coil structures to cool the rotor.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA 2394819 CA2394819A1 (en) | 2002-08-09 | 2002-08-09 | Combined pump generator and turbine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA 2394819 CA2394819A1 (en) | 2002-08-09 | 2002-08-09 | Combined pump generator and turbine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2394819A1 true CA2394819A1 (en) | 2004-02-09 |
Family
ID=31501561
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA 2394819 Abandoned CA2394819A1 (en) | 2002-08-09 | 2002-08-09 | Combined pump generator and turbine |
Country Status (1)
| Country | Link |
|---|---|
| CA (1) | CA2394819A1 (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2007085045A1 (en) * | 2006-01-27 | 2007-08-02 | Renewable Energy Systems Limited | Heat energy transfer system and turbopump |
| JP2008248830A (en) * | 2007-03-30 | 2008-10-16 | Kyushu Denshi Giken Kk | Compound turbine system and hot water power generation device using same |
| CN103410740A (en) * | 2013-09-10 | 2013-11-27 | 江苏四达动力机械集团有限公司 | Exhaust gas recirculation cooling water pump structure |
| CN105782062A (en) * | 2016-05-04 | 2016-07-20 | 广州航海学院 | Novel magnetic coupling pump device driven by excess pressure energy |
| EP3088741A1 (en) * | 2015-04-28 | 2016-11-02 | Snecma | Improved control system for a turbo pump |
| CN107503806A (en) * | 2017-08-25 | 2017-12-22 | 谢竞宁 | Turbine |
| CN109779921A (en) * | 2019-03-18 | 2019-05-21 | 李卿 | A kind of high pressure axial-flow pump |
| CN113661307A (en) * | 2019-04-05 | 2021-11-16 | 阿特拉斯·科普柯空气动力股份有限公司 | Power generation system and method of generating power by operating such a power generation system |
-
2002
- 2002-08-09 CA CA 2394819 patent/CA2394819A1/en not_active Abandoned
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2007085045A1 (en) * | 2006-01-27 | 2007-08-02 | Renewable Energy Systems Limited | Heat energy transfer system and turbopump |
| JP2008248830A (en) * | 2007-03-30 | 2008-10-16 | Kyushu Denshi Giken Kk | Compound turbine system and hot water power generation device using same |
| CN103410740A (en) * | 2013-09-10 | 2013-11-27 | 江苏四达动力机械集团有限公司 | Exhaust gas recirculation cooling water pump structure |
| EP3088741A1 (en) * | 2015-04-28 | 2016-11-02 | Snecma | Improved control system for a turbo pump |
| FR3035690A1 (en) * | 2015-04-28 | 2016-11-04 | Snecma | IMPROVED MONITORING SYSTEM FOR A PUMP |
| CN105782062A (en) * | 2016-05-04 | 2016-07-20 | 广州航海学院 | Novel magnetic coupling pump device driven by excess pressure energy |
| CN107503806A (en) * | 2017-08-25 | 2017-12-22 | 谢竞宁 | Turbine |
| CN107503806B (en) * | 2017-08-25 | 2023-12-05 | 谢竞宁 | Turbine engine |
| CN109779921A (en) * | 2019-03-18 | 2019-05-21 | 李卿 | A kind of high pressure axial-flow pump |
| CN113661307A (en) * | 2019-04-05 | 2021-11-16 | 阿特拉斯·科普柯空气动力股份有限公司 | Power generation system and method of generating power by operating such a power generation system |
| CN113661307B (en) * | 2019-04-05 | 2023-06-02 | 阿特拉斯·科普柯空气动力股份有限公司 | Power generation system and method of generating power by operating such power generation system |
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