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
  • F04D13/00—Pumping installations or systems
  • F04D13/02—Units comprising pumps and their driving means
  • F04D13/028—Units comprising pumps and their driving means the driving means being a planetary gear
• • 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
  • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
  • F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
• • 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
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
  • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
  • F05D2260/00—Function
  • F05D2260/40—Transmission of power
  • F05D2260/403—Transmission of power through the shape of the drive components
  • F05D2260/4031—Transmission of power through the shape of the drive components as in toothed gearing
  • F05D2260/40311—Transmission of power through the shape of the drive components as in toothed gearing of the epicyclical, planetary or differential type

Definitions

• the present invention relates to a kinetic turbopump for a closed circuit, in particular of a Rankine cycle type, for example a kinetic turbopump for a closed circuit, in particular of the Rankine cycle type. , especially for a motor vehicle.
• kinetic turbopump an assembly formed by a pump and a turbine.
• the pump has the particularity that its rotor carries a multiplicity of radial fins to form an impeller whose effect is the setting in rotation and the acceleration of the fluid in liquid condition.
• the turbine which is connected to the pump on the same shaft, consists of a stator part having a fixed blade called diffuser to convert the fluid pressure into a vapor condition into kinetic energy. This kinetic energy is then converted into mechanical energy through a moving blade of the rotor part of the turbine.
• the blades of the turbine consist of radial fins for the relaxation of the fluid which is ejected
• a Rankine cycle is a thermodynamic cycle by which heat from an external heat source is transmitted to a closed circuit that contains a working fluid. During the cycle, the working fluid undergoes phase changes (liquid / vapor).
• This type of cycle is generally broken down into a step during which the working fluid used in liquid form is compressed isentropically, followed by a step where the compressed liquid fluid is heated and vaporized in contact with a heat source.
• This steam is then relaxed, in another step, in an expansion machine, then, in a final step, this expanded steam is cooled and condensed in contact with a cold source.
• the circuit comprises at least one pump for circulating and compressing the fluid in liquid form, a heat exchanger evaporator which is swept by a hot fluid to effect the at least partial vaporization of the compressed fluid, an expansion machine for relaxing the steam, such as a turbine, which converts the energy of this vapor into another energy, such as an energy mechanical or electrical, and a heat exchanger-condenser by which the heat contained in the steam is transferred to a cold source, usually outside air, or a cooling water circuit, which sweeps this condenser, to transform this steam in a fluid in liquid form.
• the fluid used is generally water but other types of fluids, for example organic fluids or mixtures of organic fluids, can also be used.
• the cycle is then called Organic Rankine Cycle or ORC (Organic Rankine Cycle).
• the working fluids may be butane, ethanol, hydrofluorocarbons, ammonia, carbon dioxide, etc.
• the hot fluid for vaporizing the compressed fluid can come from various hot sources, such as a coolant (a combustion engine, an industrial process, a furnace, etc. .), hot gases resulting from combustion (fumes from an industrial process, a boiler, exhaust gas from a combustion engine or turbine, etc.), heat flow from solar thermal collectors or a geothermal source, etc.
• a coolant a combustion engine, an industrial process, a furnace, etc. .
• hot gases resulting from combustion gas from an industrial process, a boiler, exhaust gas from a combustion engine or turbine, etc.
• heat flow from solar thermal collectors or a geothermal source etc.
• the pump and the turbine are combined in one piece to form a compact turbopump.
• the shaft of this turbopump which is common to the pump and the turbine, can be rotated in several ways.
• the shaft is coupled to the crankshaft of the internal combustion engine, generally by a belt surrounding a pulley placed on this crankshaft and another pulley of link placed on this shaft, being controlled by a controlled-control coupling.
• This device thus makes it possible to turn the turbine, for a functioning configuration in a Rankine cycle circuit, in a first direction of rotation so that it acts as a turbine while being associated with the pump contained in this turbopump or, in a reverse direction of rotation, for an operating configuration in an air conditioning circuit, so that the turbine operates as a pump while being disconnected from the pump of the turbopump.
• the present invention provides a turbopump that allows the turbine to have a significantly higher rotational speed than that of the combustion engine while having a pump rotation speed lower than that of the turbine.
• the efficiency of the pump is improved by this moderate speed while the efficiency of the turbine is improved by the use of a higher speed.
• the present invention relates to a turbopump comprising a stationary housing comprising a kinetic pump with a pump rotor carried by a pump shaft and a turbine housing a turbine rotor carried by a turbine shaft.
• the pump shaft is separated from the turbine shaft and in that said turbopump comprises a speed variation device for generating a difference in rotational speed between the pump shaft and the turbine shaft.
• said turbopump comprises a speed variation device for reducing the speed of rotation of the pump shaft relative to the turbine shaft or for multiplying the speed of rotation of the shaft. of turbine relative to the pump shaft.
• the pump and turbine shafts are substantially parallel to one another.
• the speed variation device comprises a gear wheel carried by the pump shaft and a pinion carried by the turbine shaft.
• the pump and turbine shafts are substantially coaxial with each other.
• the speed variation device comprises an epicyclic gear train.
• the sun gear of the epicyclic gear is carried by the turbine shaft.
• the planet carrier of the epicyclic gear is carried by a fixed wall of the turbopump housing.
• the planet carrier of the epicyclic gear is carried by the pump shaft.
• the ring of the epicyclic gear is carried by a fixed wall of the turbopump housing.
• the ring of the epicyclic gear is carried by the pump shaft.
• it comprises a connecting pulley carried by the pump shaft.
• the turbopump comprises a controlled-controlled coupling for connecting the connecting pulley and the pump shaft.
• the turbopump comprises a speed variation means between the turbine shaft and a connecting pulley.
• the invention comprises an electric machine driving the pump shaft.
• the invention relates to an application of a turbopump according to one of the preceding characteristics to a closed circuit, in particular of the Rankine or ORC (Organic Rankine Cycle) type.
• FIG. 1 which shows a sectional view of an embodiment of a turbopump according to the invention
• FIG. 2 which is a sectional view of another embodiment of a turbopump according to the invention.
• FIG. 1 shows a turbopump 10 for a closed circuit, in particular of the Rankine cycle type, in particular for a motor vehicle.
• the turbopump 10 which is here a kinetic turbopump, comprises a stationary housing 12 which houses the rotating part 14 (or rotor) of a means for circulating and compressing a fluid 1 6, called a pump, carried by a pump shaft.
• pump 18 and another fixed housing 12 'housing the rotating part 20 (or rotor) of a means of expansion of a compressed fluid 22, said turbine, carried by a turbine shaft 24.
• the turbopump has the particularity that the two shafts 18 and 24 are separated from one another and are placed above one another substantially parallel to each other. the other.
• the two shafts are separated (or distinct) from one another and are connected to one another by a speed variation device 26 which makes it possible to generate a speed difference of rotation between the pump shaft and the turbine shaft.
• the function of the speed variation device is to multiply the speed of rotation between the pump shaft and the turbine shaft when the pump shaft gives the rotational speed pulse or to reduce the speed. rotation between the turbine and the pump when the turbine shaft generates the rotation speed, as will be explained in detail in the following description.
• the speed variation device comprises a gear train 28 with a gear wheel 30, of large diameter, carried by the pump shaft 18 and which cooperates with a pinion 32, of smaller diameter than that of the wheel, carried by the turbine shaft 24, the wheel and the pinion being advantageously placed in the same vertical plane.
• the difference in diameter between the wheel and the pinion thus makes it possible to produce a speed ratio between the two shafts, this speed ratio preferably being between 2 and 6 in the context of the present invention.
• This turbopump also comprises a link pulley 34 which is rotatably connected to the pump shaft 18 through a controlled-control coupling 36, here an electromagnetic type clutch.
• This pulley is controlled in rotation by a band closed on itself, such as a chain or a connecting belt 38.
• This band is advantageously connected to a crankshaft pulley which is connected in rotation with the crankshaft of an internal combustion engine (not shown).
• An alternative is to replace the mechanical connection (pulley and electromagnetic clutch) by an electric generator so as to constitute a turbo-pump-generator.
• turbopump as described above can be used in many fields, such as oilfields, aeronautics, automobiles ...
• This turbopump finds its application more particularly with a closed circuit, in particular of Rankine cycle type 40 as illustrated in FIG.
• This Rankine cycle closed circuit is advantageously of the ORC (Organic Rankine Cycle) type and uses an organic working fluid or mixtures of organic fluids, such as butane, ethanol and hydrofluorocarbons.
• ORC Organic Rankine Cycle
• closed circuit can also operate with a fluid such as ammonia, water, carbon dioxide ...
• the outlet 42 of the pump 1 6 is connected to an inlet 44 of a heat exchanger 46, called evaporator, which is traversed by the working fluid compressed by the pump and through which the working fluid reaches the outlet 48 of this evaporator in the form of compressed steam.
• evaporator a heat exchanger 46
• This evaporator is also traversed by a hot source 50, in liquid or gaseous form so as to transfer its heat to the working fluid.
• This hot source makes it possible to carry out the vaporization of the fluid and can come from various hot sources, such as a cooling liquid of a combustion engine, an industrial process, a furnace, hot gases resulting from combustion (exhaust gas from a combustion engine, fumes from an industrial process, a boiler, or a turbine, etc.), heat flux from solar thermal collectors, geothermal source, etc.
• the outlet of the evaporator is connected to an inlet 52 of the turbine 22 to admit the working fluid in the form of vapor compressed at high pressure, this fluid emerging through an outlet 54 of this turbine in the form of low-pressure vapor pressure.
• the outlet of the turbine is connected to an inlet 56 of a cooling exchanger 58, or condenser, which makes it possible to transform the low-pressure vapor it receives into a low-pressure liquid fluid to introduce it to an inlet 60 of the pump.
• This condenser is swept by a cold source, usually a flow of ambient air or cooling water, so as to cool the expanded steam so that it condenses and turns into a liquid.
• a cold source usually a flow of ambient air or cooling water
• the shaft 18 is coupled to the connecting pulley 34 of the turbopump by the clutch 36.
• the rotational movement of the crankshaft is then transmitted to the connecting pulley 34 by the connecting belt 38. This movement of rotation is then relayed back to the pump shaft and the pump rotor.
• the toothed wheel 30 meshes with the pinion 32.
• the shaft 24 of the turbine rotates at a speed greater than that of the pump shaft and thus the turbine rotates at a higher speed than that of the pump.
• the speed variation device 26 thus has a speed multiplier function between the pump and the turbine.
• the turbine After this start-up phase, the turbine produces more power than the consumption of the pump and consequently this turbine then becomes the generating element of rotational movement to the detriment of the pump.
• the internal combustion engine is still operational and the shaft 18 is coupled to the pulley 34 of the turbopump via the clutch 36.
• the power generated by the turbine 22 is transmitted to the pinion 32 which transmits it to the toothed wheel 30 and then to the pulley 34 of the turbopump.
• the power of the pulley 34 is then transmitted by the belt 38 to the crankshaft pulley which will bring extra power to the crankshaft and therefore to the internal combustion engine. This goes therefore to assist the work requested the engine and thus reduce the fuel consumption of the engine.
• the speed variation device 26 has a speed reduction function between the turbine shaft and the pump shaft.
• the turbopump 1 which is also a kinetic turbopump, comprises a fixed housing 1 12 which houses a rotor 1 14 of a pump 1 1 6 carried by a pump shaft 1 18, and a rotor 120 of a turbine 1 22 carried a turbine shaft 124.
• the shafts of the pump and the turbine are separated from each other while being in the extension of one another, and preferably coaxially.
• the shaft of the pump 1 18 coaxially passes through the shaft of the turbine 124, which is thus hollow, to open beyond the turbine.
• the two shafts are connected to one another by a speed variation device 1 26.
• This device also makes it possible to generate a difference in speed of rotation between the pump shaft and the turbine shaft.
• the function of the speed variation device is to multiply the speed of rotation between the pump shaft and the turbine shaft when the pump shaft gives the speed pulse. rotating or reducing the speed of rotation between the turbine and the pump when the turbine shaft generates the rotational speed as will be explained in detail in the following description.
• This speed variation device comprises an epicyclic gear train 128 whose sun gear 130 is carried by the hollow shaft of the turbine 124, whose ring 132 is carried by the pump shaft 1 18, and whose planet carrier 134 is carried by a vertical wall 135 of the housing 1 12.
• This turbopump also comprises a link pulley 136 which is rotatably connected to the pump shaft 1 18 through a controlled-control coupling 138, of the electromagnetic clutch type, and which is rotated by a closed band on it. itself, such as a chain or a connecting belt 140.
• This band is advantageously connected to a crankshaft pulley which is connected in rotation with the crankshaft of an internal combustion engine (not shown).
• this turbopump more particularly finds its application for a closed circuit, in particular of the Rankine cycle type.
• the outlet 142 of the pump 1 16 is connected to an inlet of an evaporator, which is traversed by the working fluid compressed by the pump, the outlet of the evaporator is connected to an inlet 144 of the turbine 122 for admitting the working fluid in the form of vapor compressed at high pressure, this fluid emerging through an outlet 146 of the turbine in the form of low-pressure expanded steam.
• the outlet of the turbine is connected to an inlet of a condenser, which makes it possible to convert the low-pressure vapor it receives into a low-pressure liquid fluid to introduce it to an inlet 148 of the pump.
• the internal combustion engine is operational and it is necessary to prime the pump 1 1 6 of the turbopump.
• the shaft 1 18 is coupled to the connecting pulley 136 of the turbopump by the clutch 138.
• the rotational movement of the crankshaft is then transmitted to the connecting pulley by the connecting belt 140.
• This rotational movement is then retransmitted to the pump shaft and the pump rotor as well as to the ring gear 132 of the planetary gear train 128.
• this crown meshes with the planet carrier which is fixed.
• the rotation movement of the satellites of this planet carrier is communicated to the sun gear 130 and then to the shaft of the turbine.
• the planetary gear train has a speed ratio that increases the speed of the sun gear relative to that of the crown. By this the turbine rotates at a speed greater than that of the pump.
• the epicyclic train 128 thus has a speed multiplier function between the pump and the turbine with a first multiplier speed ratio for the turbine with a rotational speed transmission between the crown, the planet carrier and the sun gear.
• the turbine After this start-up phase, the turbine produces more power than the consumption of the pump and consequently this turbine then becomes the generating element of rotational movement to the detriment of the pump.
• the internal combustion engine is still operational and the shaft 1 18 is coupled to the pulley 136 of the turbopump by the clutch 138.
• the power generated by the turbine 122 is transmitted to the sun gear 130 which transmits it to the ring gear 132 through the planet carrier 134.
• the power of the ring gear is transmitted to the turbine shaft and to the pulley 136 of the turbopump.
• the power of the pulley is then transmitted by the belt 140 to the crankshaft pulley which will bring extra power to the crankshaft and therefore to the internal combustion engine.
• the speed variation device 126 has a speed reduction function between the turbine shaft and the pump shaft with a first reduction ratio for the pump with a transmission of rotation between the sun gear, the planet carrier and the crown.
• the advantage of this configuration is to allow the turbine a rotational speed much higher than the rotational speed of the motor and the pump, which is favorable to the efficiency of the turbine.
• FIG. 3 comprises the same elements as those of FIG. 2 but with a particular arrangement of the epicyclic gear train 128.
• the sun gear 130 is carried by the hollow shaft of the turbine 124
• the ring 132 is carried by a vertical wall 135 of the housing 1 12
• the planet carrier 134 is carried by the shaft of the pump 1 18.
• This operation of this epicyclic gear configuration is similar to that of FIG. 2 with a speed multiplier function between the pump and the turbine, with a second multiplier speed ratio for the turbine, during the transmission of rotation speed between the planet carriers, the crown, and the sun gear.
• the variant of Figure 4 also comprises the same elements as those of Figure 2 or 3 but with a particular arrangement of the epicyclic gear train 128, which is housed between the turbine and the pump.
• the epicyclic gear train comprises the same arrangement as that of FIG. 2 with the sun gear 130 carried by the hollow shaft of the turbine 124, the ring gear 132 carried by the shaft of the pump 1 18, and the carrier satellites 134 is carried by the vertical wall 135 of the housing 1 12.
• this epicyclic train configuration is identical to that of FIG. 2 with a speed multiplier function between the pump and the turbine with a first multiplier speed ratio for the turbine with a rotational speed transmission between the carrier and the turbine.
• the main advantage of this variant lies in the distance of the pump and the turbine, which limits the heat exchange between the hot parts of the turbine and the pump, resulting in improved performance.
• the epicyclic train is also disposed between the pump and the turbine as for the variant of Figure 4 but with a particular arrangement of the epicyclic gear train 128.
• the sun gear 130 is carried by the hollow shaft of the turbine 124, the ring 132 is carried by a vertical wall 135 of the housing 1 12, and the planet carrier 134 is carried by the shaft of the pump 1 18.
• This operation of this epicyclic train configuration is similar to that of FIG. 4 with a speed multiplier function between the pump and the turbine, with a second multiplier speed ratio for the turbine, when transmitting rotational speed between the turbine and the turbine. planet carriers, the crown, and the sun gear.
• FIG. 6 differs from FIG. 2 only in the arrangement of the turbine 122, which is reversed, with the inlet 144 of the turbine which is situated on the side of the epicyclic gear train 128 and its output 146 on the side of the pump 1 1 6.
• This embodiment allows to juxtapose the large turbine diameter and the epicyclic train, facilitating a more compact design.
• the epicyclic train 128 is also placed between the pump 1 1 6 and the turbine 122.
• the pump 1 1 6 is housed between the train 128 and the connecting pulley 136 while the turbine is placed below this same train.
• the pump shafts 1 18 and turbine 124 are separated from each other while being coaxial and in the extension of one another.
• the epicyclic gear train 128 is mounted between these two shafts with the ring gear 132 carried by the pump shaft 1 18, the sun gear 130 carried by the turbine shaft 124 and the planet carrier 134 carried by a fixed wall 150 of the housing 1 12.
• Figure 8 differs from Figure 7 in that the ring 132 is carried by a fixed wall 150 of the housing 1 12, the sun gear 130 is carried by the turbine shaft 124 and the planet carrier 134 is worn by the pump shaft 1 18.
• FIG. 7 also makes it possible to perform a speed multiplier function between the pump and the turbine with a second multiplier speed ratio for the turbine with a rotational speed transmission. between the planet carrier, the ring gear, and the sun gear, and a speed reduction function between the turbine and the pump with a first reduction gear ratio between the sun gear, the planet carrier and the crown

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• Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Supercharger (AREA)
• Engine Equipment That Uses Special Cycles (AREA)

Applications Claiming Priority (2)

Publications (1)

Family

ID=60081054

Family Applications (1)

Country Status (4)

Family Cites Families (12)

• 2017
  • 2017-09-06 FR FR1758211A patent/FR3070725B1/fr active Active
• 2018
  • 2018-08-30 WO PCT/EP2018/073300 patent/WO2019048319A1/fr not_active Ceased
  • 2018-08-30 EP EP18758889.2A patent/EP3679253A1/de not_active Withdrawn
  • 2018-08-30 JP JP2020513623A patent/JP2020532679A/ja active Pending

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