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WO2020011790A1 - Procédé pour faire fonctionner un générateur linéaire à piston libre - Google Patents

Procédé pour faire fonctionner un générateur linéaire à piston libre Download PDF

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Publication number
WO2020011790A1
WO2020011790A1 PCT/EP2019/068421 EP2019068421W WO2020011790A1 WO 2020011790 A1 WO2020011790 A1 WO 2020011790A1 EP 2019068421 W EP2019068421 W EP 2019068421W WO 2020011790 A1 WO2020011790 A1 WO 2020011790A1
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WO
WIPO (PCT)
Prior art keywords
piston
linear generator
rotor
combustion
combustion chamber
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/EP2019/068421
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German (de)
English (en)
Inventor
Martin Reber
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Individual
Original Assignee
Individual
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of WO2020011790A1 publication Critical patent/WO2020011790A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B63/00—Adaptations of engines for driving pumps, hand-held tools or electric generators; Portable combinations of engines with engine-driven devices
    • F02B63/04—Adaptations of engines for driving pumps, hand-held tools or electric generators; Portable combinations of engines with engine-driven devices for electric generators
    • F02B63/041—Linear electric generators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B11/00—Reciprocating-piston machines or engines without rotary main shaft, e.g. of free-piston type
    • F01B11/007—Reciprocating-piston machines or engines without rotary main shaft, e.g. of free-piston type in which the movement in only one direction is obtained by a single acting piston motor, e.g. with actuation in the other direction by spring means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B11/00—Reciprocating-piston machines or engines without rotary main shaft, e.g. of free-piston type
    • F01B11/02—Equalising or cushioning devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B71/00—Free-piston engines; Engines without rotary main shaft
    • F02B71/04—Adaptations of such engines for special use; Combinations of such engines with apparatus driven thereby
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/18—Structural association of electric generators with mechanical driving motors, e.g. with turbines
    • H02K7/1869—Linear generators; sectional generators
    • H02K7/1876—Linear generators; sectional generators with reciprocating, linearly oscillating or vibrating parts
    • H02K7/1884—Linear generators; sectional generators with reciprocating, linearly oscillating or vibrating parts structurally associated with free piston engines
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02P—CONTROL OR REGULATION OF ELECTRIC MOTORS, ELECTRIC GENERATORS OR DYNAMO-ELECTRIC CONVERTERS; CONTROLLING TRANSFORMERS, REACTORS OR CHOKE COILS
    • H02P25/00—Arrangements or methods for the control of AC motors characterised by the kind of AC motor or by structural details
    • H02P25/02—Arrangements or methods for the control of AC motors characterised by the kind of AC motor or by structural details characterised by the kind of motor
    • H02P25/06—Linear motors
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02P—CONTROL OR REGULATION OF ELECTRIC MOTORS, ELECTRIC GENERATORS OR DYNAMO-ELECTRIC CONVERTERS; CONTROLLING TRANSFORMERS, REACTORS OR CHOKE COILS
    • H02P9/00—Arrangements for controlling electric generators for the purpose of obtaining a desired output
    • H02P9/04—Control effected upon non-electric prime mover and dependent upon electric output value of the generator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B23/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
    • F01B23/10—Adaptations for driving, or combinations with, electric generators

Definitions

  • the present invention relates to methods for operating a free piston linear generator (hereinafter also referred to as FKLG ⁇ ) for generating electrical energy and a FKLG.
  • FKLG ⁇ free piston linear generator
  • Known FKLG generally comprise a linear generator such as a combustion unit with a combustion chamber, the combustion unit and the linear generator being coupled to one another via at least one piston-rotor unit, which comprises a piston that has an expansion stroke of one Execute top dead center to a bottom dead center and, using a gas pressure spring, a compression stroke from bottom dead center to top dead center ⁇ .
  • a linear generator such as a combustion unit with a combustion chamber
  • the combustion unit and the linear generator being coupled to one another via at least one piston-rotor unit, which comprises a piston that has an expansion stroke of one Execute top dead center to a bottom dead center and, using a gas pressure spring, a compression stroke from bottom dead center to top dead center ⁇ .
  • the FLKG is understood as a resonant circuit in which the kinetic energy of a piston is repeatedly converted into gas pressure ⁇ , and vice versa.
  • the gas pressure can either be built up in the gas pressure spring or in the combustion chamber for compression ⁇ .
  • second-order resonant circuits see also pendulum
  • a system with these basic properties is hardly suitable for controlling and regulating the piston speeds and thus the thermal process in detail at any time or at any piston position.
  • DE 1 1 2012 000 915 T5 and DE 10 2014 001 770 Al disclose a method for operating a free-piston linear generator for generating electrical energy
  • the free-piston linear generator for at least one linear generator and at least one combustion unit with at least one combustion chamber and ⁇ and the combustion unit ⁇ and the linear generator are coupled to one another via at least one piston-rotor unit ⁇
  • the piston-rotor unit ⁇ comprising at least one rotor and at least one piston ⁇ , which extends an expansion stroke from a top dead center Execute a bottom dead center and a compression stroke from bottom dead center to top dead center, whereby after the acceleration of the at least one piston, the electrical energy extraction by the linear generator is regulated or controlled in such a way that this results in a controlled setpoint speed profile of the piston between top dead center and bottom dead center t point is reached at least in sections.
  • DE 102 19 549 A1 uses oily fuels for the lubrication of individual or all plain bearings, which are supplied to the combustion after lubrication. From DE 10 2016 109 029 A1, auto-ignition operation by compression ignition is known.
  • the present invention is based ⁇ the task of creating a method for operating an FLKG which eliminates the aforementioned problems ⁇ and which is suitable for the compression stroke from bottom dead center to top dead center without the exclusive use of a gas pressure spring or electrical energy.
  • the present invention describes ⁇ a method for operating an FLKG, which has at least one linear generator and at least one combustion unit ⁇ with at least one combustion chamber ⁇ , the combustion unit ⁇ and the linear generator being coupled to one another via at least one piston-rotor unit ⁇ , which comprises at least one piston ⁇ , which carries out an expansion stroke from TDC to TDC and a compression stroke from TDC to TDC ⁇ , whereby after the acceleration of the at least one piston, the electrical energy consumption is regulated by the linear generator in such a way that a re gulation of the speed of the piston between OT and UT is reached ..
  • the aforementioned method is characterized in that the energy for executing the compression stroke is taken from the linear generator, which energy during the expansion stroke in the linear generator is magnetically stored energy provides, the magnetically stored energy available for compression in the linear generator at UT can be supplemented by additional energy storage in the form of a gas pressure spring or electrical energy.
  • Figure 1 shows the basic structure of the FKLG according to the invention in a preferred embodiment as a single-piston system with traditional valve train in the cylinder head.
  • the partially acting gas pressure spring serves to reverse the movement of the piston or rotor. It is said to have no effect if the piston is not near UT.
  • Optional valves ensure pressure equalization and cooling when air moves through the ring-shaped air gaps at the rotor / stator and plunger / pressure chamber of the gas pressure spring;
  • FIG. 2a shows an ideal typical speed profile piston / rotor under Normlas ⁇ ; Rapid pressure reduction after ignition and maximum rapid cooling of the combustion gases are achieved by withdrawing electrical energy as late as possible in the DeAcc phase; This profile is of a theoretical nature and can usually not be implemented in practice if the electrical generator cannot extract the required amount of energy in the short period of the DeAcc phase.
  • Fig. 2b an ideal typical speed profile piston / rotor under maximum load ⁇ ; rapid pressure reduction after ignition and max. Rapid cooling of the combustion gases is achieved by withdrawing electrical energy as late as possible in the Cons ⁇ and DeAcc phases.
  • Thisnicsprolf can in practice simple U m ⁇ a backing than the profile in Fig. 2.a because the electric generator, the exception from the required amount of energy over a longer period of OT to the end of phase DeAcc can split.
  • Fig. 2c shows an ideal typical speed profile piston / rotor under partial load, this profile is also theoretical in nature and can usually not be implemented in practice if the electric linear generator can not take the required amount of energy in the short period of time of the DeAcc phase ;
  • Fig. 3 shows the basic structure of the FKLG in a further embodiment form as a two-piston system, mirror image of inlet / outlet valves on the cylinder wall;
  • Figure 4 shows the arrangement of the inlet and outlet valves in pairs on the cylinder wall with inlet and outlet channels behind it.
  • Figure 5 shows the fuel injection for FKLG operation with diesel auto-ignition at comparatively low pressures (100 to 200 bar).
  • Fig. 6 shows a combined lubrication and fuel system for FKLG operation with diesel auto-ignition at comparatively low pressures (100 to 200 bar) when using oily fuels;
  • Fig. 7 is a lubrication system for the FKLG when operating with oily fuels. Lubrication with fuels that are constantly renewed;
  • FIG. 10 shows a simulated speed profile of the piston / rotor with reluctance spring and linear energy extraction.
  • the energy consumption is proportional to the overlap of rotor and stator (max. At TDC, min. At UT) and brakes the piston to Vmin.
  • the reluctance spring brakes to a standstill of the piston and ensures ⁇ the reversal of movement;
  • the reluctance spring supplies the piston with even energy over the distance UT to OT, which is why the piston speed increases comparatively slowly after UT;
  • Figure 1 1 shows a simulated speed profile of the piston / rotor with reluctance spring and controlled energy consumption, reduced energy consumption in the area between TDC and LDC;
  • the pattern of energy consumption must be designed so that the piston speed adjusts to the maximum piston speed over the longest possible distance to TDC ⁇ .
  • the piston position can be observed using conventional methods, for example by means of light barriers.
  • the induction voltages in the stator can also be observed to estimate the piston speed
  • Fig. 12 shows a cross section through the stator and rotor with radial flow guidance and the flow distribution when rotor (in this consisting of outer and inner sleeve) sweeps over the stator ⁇ ;
  • Fig. 13 an exemplary structure of the stator and rotor (consisting of inner and outer rotor) with radial flow control, the generator and motor operation supports ⁇ .
  • the electrical machine consists of several such polar planes rotated and stacked by 60 °; 14 shows an alternative exemplary construction of the electrical machine with radial flow guidance, consisting of an inner stator and an outer rotor, which supports generator and motor operation.
  • the complete electrical machine consists of several pole planes rotated and stacked at 60 °. It is easy to see how the geometry of the stator contributes to an increase in the magnetic fluxes in the magnetically active gap;
  • stator and rotor with radial flow guidance, which supports generator and motor operation.
  • Runners in cylindrical shape, whose magnetically active surfaces border on the inner and outer stator. Simulation with permanent magnets made of ferrite, ie without using permanent magnets made from rare earths, such as neodymium;
  • Fig. 1 6 shows an electrical generator with axial flow guidance in the rotor (cross-sectional drawing).
  • the cylindrical rotor poles can be seen with soft magnetic material of different thickness.
  • the ring coils in the stator can be operated individually, in series or in parallel on the rectifier depending on the position and speed of the rotor.
  • Phase 1 Ignition and heating of the filling gas
  • the linear generator 10 should preferably be designed so that it can help the piston 120 in position after ignition near TDC or at least complicates the absorption of kinetic energy until the combustion process is completed and the maximum temperature of the combustion gas is reached. The linear generator 10 should therefore be able to absorb the maximum electrical energy, particularly near OT.
  • This design of the electric generator for maximum power development and energy consumption near TDC prevents a too fast speed rise near TDC and ⁇ ensures that the combustion is largely ⁇ completed before the piston reaches its maximum speed. It is therefore desirable and therefore particularly advantageous to have maximum folding forces for the piston 120 close to TDC until the end of the complete combustion with the aid of the generator coils in the stator 100, which for this purpose can exert particularly high holding forces on the rotor 121 by means of electromagnetic action at rotor positions near TDC. The maximum possible holding forces result from the fact that the rotor is completely submerged in the stator ⁇ at TDC.
  • Phase 2 acceleration of the piston and maximum electrical energy consumption
  • the speed profile of the piston should ideally have a shape as in FIG. 2a.
  • ideal speed profiles are established as in FIGS. 2b and 2c.
  • the linear generator 10 is preferably to be designed such that the appropriately controlled energy extraction, especially at the end of phase 2, adjusts the speed profile shown in FIG. 2b ⁇ .
  • the ideal linear generator 10 and the control 101 are designed so that with a minimum piston or rotor weight, a speed profile as in FIG. 2b is set.
  • the energy consumption at the generator correlates with the energy released in the thermal process, is at a maximum after OT and decreases towards UT.
  • the high speed of the piston which remains constant over long distances after OT, enables ⁇ a consistently high efficiency for the electrical generator and helps to minimize thermal losses.
  • stator coils in a generator with axial flow guidance are advantageously so optimized with different numbers of turns and conductor cross sections that a sufficiently high voltage is generated with a speed profile according to FIG. to be able to tap the required energy with high electrical efficiency at different or lower rotor speeds.
  • Phase 2 will therefore allow the piston 120 to accelerate as quickly as possible after the completion of the combustion, in order to slow it down towards the end of phase 2 to such an extent that it still has sufficient kinetic energy in order to reverse movement, including gas outlet and final pressure reduction ( Phase 3), gas exchange and compression (phase 4), to enable a sufficiently high compression for a safe next ignition.
  • Phase 3 gas outlet and final pressure reduction
  • phase 4 gas exchange and compression
  • Phase 3 Reversal of movement with outlet and final pressure reduction of the cooled useful gas
  • phase 3 After the end of the electrical energy extraction in phase 2, phase 3 begins. In phase 3, rotor 121 and piston 120 are to experience the reversal of their direction of movement. The piston speed when entering and exiting in phase 2 should be as equal as possible, only the direction has to be reversed.
  • the exhaust valves 124 can also be opened so that the final pressure reduction in the piston chamber is initiated ⁇ .
  • FIG. 3 A device suitable for reversing the direction of movement by means of partially acting gas pressure spring 13 is shown in FIG. 3.
  • the stamp of the gas pressure spring 13 strikes the pressure chamber 130 of the gas pressure spring 13 shortly before UT, so that the pressure required for the movement reversal builds up.
  • the play between the plunger and the pressure chamber 130 ensures that air escapes when the pressure in the gas pressure spring 13 builds up, which air is fed in again from the outside through the pressure valves. This creates an air flow in the air space of the electrical machine around the rotor, which can be used for cooling purposes.
  • the Slider 121 is only a small part of stator 100 at position UT.
  • Phase 4 renewal of the filling gas and compression
  • phase 4 the piston 120 is again on its way to TDC.
  • the inlet valves 123 must now open and fresh gas must flow in at a suitable pressure.
  • inlet 123 and outlet valves 124 close as long as piston 120 is still sufficiently white from TDC ⁇ .
  • the combustion process at OT in phase 1 can be initiated again ⁇ .
  • the present system is advantageously combined with a turbo charger including charge air cooler.
  • the turbocharger would generate the pressure required to introduce the fresh gas in phase 4.
  • the single-piston systems as in Fig. 1 generate many undesirable vibrations and shrinkages. This problem can be effectively countered with a two-piston system if both pistons 120 move in opposite directions on one axis.
  • two opposed pistons 120 are operated with a common combustion chamber (FIG. 3).
  • the common combustion chamber 1 10 offers the advantage that there is only one common “hot” end for both pistons 120 ⁇ .
  • this solution also requires that the valves for gas inlet 46a and outlet 46b be arranged on the common cylinder wall. This offers ⁇ the advantage that incoming and outgoing gases in the combustion chamber can rotate while moving, similar to a cyclone.
  • the rotational movement contributes to the quick and clean gas exchange, ensures the separation of fresh and exhaust gas and promotes rapid combustion after (auto) ignition.
  • the rotational movement of the gas masses 20 also contributes to the fact that fuel clouds introduced into the combustion chamber are concentrated in the center of rotation with droplets of different sizes, predominantly larger droplets being deposited on the walls of the combustion chamber and thus producing fewer pollutants, soot and fine dust.
  • the rotational speed of the gas masses 20 can be increased if the gas masses 20 are brought into a space with a smaller diameter.
  • the shape of the inflow and outflow channels behind the valves 123, 124 (see FIG. 4) generate the desired rotating air masses during gas exchange.
  • the shape of the piston 120 (for example with a depression in the middle) accelerates the rotation of the air masses as part of the compression. Venfilan firing with a Blafffeder / Venfilefä Trent around the cylinder
  • the ring-shaped arrangement of the inlet 123 and outlet valves 124 according to FIG. 4 enables a particularly effective form of venfil attachment by means of a circumferential leaf spring 14.
  • the movable and circumferential leaf spring 14 is mounted on a guide ring 140 ⁇ and press ⁇ the valve after closing in the seat.
  • a guide roller 141 is attached to the Venfilsfäßel ⁇ over the leaf spring 14 ⁇ , so that the contact pressure do not assemble until the valve has already reached its position in the valve seat ⁇ .
  • a second guide roller 142 is mounted on the Venfilsfäßel under the leaf spring 14, so that the moving leaf spring 14 can push the valve into the combustion chamber to open it. This happens ⁇ with the sliding leaf spring 14 without great effort.
  • the distance between the upper and lower guide rollers 141 is constant and the thickness of the leaf spring 14 is designed so that it can move in any position without play between the guide rollers 141.
  • the circumferential leaf springs 14 are mounted on a guide ring ⁇ , which is also responsible for the propulsion.
  • the guide ring is broken into the desired position using a gear and stepper motor ⁇ .
  • two circumferential leaf springs 14 with guide rollers 141 on the right and left of the Venfilsficideels are required ⁇ . These two rotating leaf springs 14 can be moved in the same or opposite directions. If the lower guide roller 141 for inlet 123 and outlet valves 124 is only attached to a soap of the Venfilsfössel, one of the two circumferential leaf springs 14 (e.g. the upper) can open the inlet valve 123 and the other (e.g.
  • both leaf springs 14 press all valves 123, 124 back into their seats with both upper guide rollers.
  • the actuation of the valves 123, 124 by means of rotating blade springs 14 also has the advantage that the temperature-dependent length variation of the Venfil tappet is automatically compensated ⁇ . Maintenance-intensive work such as adjusting the valve clearance or complex solutions such as tappets are avoided.
  • the leaf spring combines ⁇ the function of valve spring and valve control. Implementations with valve springs / spiral springs per valve are also conceivable and rotating control element ⁇ ("rotating camshaft”) which presses on the valve stem by means of protuberances / cams in the rotating ring to open the valve ⁇ .
  • the fuel system operation with compression ignition
  • the fuel system is described below (Fig. 5).
  • the fuel pump ⁇ brings the fuel to a comparatively low pressure of 100 to 200 bar (depending on the fuel).
  • the fuel prepared in this way is cooled and injected by direct injection into the combustion chamber of the combustion chamber 110 as soon as the inlet valves 123 are closed.
  • the fuel after injection as an atomized fuel cloud, mainly collects in the center of rotation of the gas masses 20 before it evaporates when the pressure rises further. Larger droplets of fuel condense on the cylinder wall.
  • the evaporation energy of the fuel is also used to cool the fresh gas already in the combustion chamber as far as possible.
  • the FKLG comes with only two plain bearings (Fig. 1 and Fig. 3).
  • plain bearing 1, GL1 In addition to the piston rings (plain bearing 1, GL1), another plain bearing (GL2) is required for the push rod 125 ⁇ , which is connected on one side to the piston 120 and on the other side to the rotor 121 of the electrical system.
  • lubricant is applied to surfaces sliding against each other, especially on the running surfaces of the piston rings and on the push rod 125. Since the arrangement ⁇ does not make any special demands on the absorption of lateral forces ⁇ , it is not necessary to use high-quality lubricating oil ⁇ . In addition, oily fuel can be used, the lubricating properties (viscosity) of which already ensure safe and wear-free operation for sufficient lubrication.
  • lubricate the valves and the associated mechanical components with oily fuels.
  • the arrangement becomes maintenance-free if the fuel which has been brought in for lubrication is supplied at regular intervals or continuously for combustion.
  • Fig. 7 shows a branch that feeds the fuel after passing through the filter unit of the injection pump, and thus the combustion ⁇ .
  • the arrangement (Fig. 6 and Fig. 7) does not need to be treated separately and partly problematic for the environment lubricating oils. Used lubricating oils do not have to be exchanged ⁇ or disposed of at great expense.
  • an embodiment according to FIG. 8 is suitable for the lubrication.
  • a key component of the invention is the electrical machine, which is given by the push rod 125 under the piston 120.
  • the push rod is connected to the rotor 121 of the machine.
  • thermal insulation is provided (e.g. ceramic disc 126, thermal conductivity ceramic porcelain: typically 1.5 W / (mK), various thermal conductivity aluminum: typically 235 W / ( mK)) inserted.
  • the rotor 121 itself contains no permanent magnets and in the simplest case the cylindrical rotor structure consists of soft magnetic iron (sheet package made of electrical sheets) without further structuring.
  • the piston movement pushes the cylindrical rotor 121 (designs as single or double cylinders are possible) over the likewise cylindrical stator 100, so that a magnetically active gap 122 arises between the rotor and stator surfaces ⁇ .
  • rotor 121 and stator 100 are completely pushed over one another, and the surfaces of rotor 121 and stator 100 at gap 122 are completely coincide with maximum area.
  • the rotor and stator surfaces preferably overlap only minimally.
  • the rotor 121 Since the stator has 100 permanent magnets ⁇ , which flow the gap 122 with a magnetic field (axial and / or radial) in the de-energized state, the rotor 121 will always experience a force towards TDC if the overlap is not complete.
  • This reluctance force is only dependent on the gap width, the gap length (circumference) and the amount of the additional magnetic field built up in it with progressive coverage of the stator and rotor surfaces. In the present arrangement, this reluctance force is used to move the rotor 121 without current from the UT position to the OT position and to apply the necessary compression work in the process.
  • the “reluctance spring” constructed in this way can reverse the movement without the support of a gas pressure spring 13.
  • the piston 121 In the work cycle with the piston movement from TDC to TDC, the piston 121 must also work against the reluctance force in a construction according to FIG. 1 or FIG. 3. Reluctance force and the withdrawal of electrical energy during the work cycle lead to the piston 120 and rotor 121 being completely braked at UT, and a new compression cycle can be started.
  • the reluctance force is used in the present invention in order to partially or completely replace the function of the gas pressure spring 13 which is normally used in an FKLG.
  • An FKLG which can do without gas pressure springs 13 for the piston return by using reluctance forces of the electrical machine, is intended here as a reluctance-free-piston linear generator (R-FKLG) denote ⁇ .
  • R-FKLG reluctance-free-piston linear generator
  • FIG. 10 and 11 show simulated speed profiles of the piston 120 of an R-FKLG 1 as a function of the profile of the electrical energy extraction.
  • FIG. 11 shows that the piston speed can be kept approximately at Vmax over long distances by skillful electrical energy extraction from the linear generator 10.
  • the rotor 121 is a cylinder made of soft magnetic materials (e.g. electrical sheets). In particular, it contains neither coils / conductor loops nor permanent magnets.
  • the stator 100 with radial flux guidance preferably contains disk-shaped, rectangular permanent magnets (PM) 1001 in a star-shaped arrangement in order to flood the iron pacts between the permanent magnets 1001 with a magnetic field strength.
  • the permanent magnets te 1001 are surrounded tangentially to the magnetic flux direction to the side of the magnetic gap with coil packets (see FIG. 12).
  • the pole faces of the permanent magnets 1001 emit the magnetic flux of the PMs 1001 into the iron pacts of the stator 100.
  • the iron packets between the PMs 1001 collect the magnetic flux, so that even weak PMs on the pole faces of the stator 100 can generate large magnetic fluxes if the PMs 1001 are only long enough (or the stator is thick enough).
  • the stator geometry thus bundles the magnetic fluxes of the PMs 1001 in order to generate high magnetic fluxes in the magnetic gap 122.
  • FIG. 12 also shows how a radial magnetic flux is formed around the coils 1000 ⁇ , provided that the rotor sweeps over the stator 100 ⁇ . If piston 120 is moved from OT to UT ⁇ , the swept area of stator 100 and rotor 121 decreases and the magnetic fields exposed to the coil conductors decrease. The coil conductors answer ⁇ with an induction current so that electrical power can be drawn in the work cycle.
  • the field lines in the external rotor are particularly strong in the vicinity of the coil conductors. It is therefore advisable to increase the rotor thickness at these points and to reduce the thickness of the rotor 121 between the coil conductors. This creates a weight-optimized runner 121 that promises higher performance and lower power loss.
  • stator 100 and rotor 121 are at a maximum overlap of the rotor 121 and stator 100 in the 122 gap and tend towards zero with little overlap (only leakage flux).
  • the magnetic fluxes change their amount in this arrangement, but not their polarity. In rotor 121 and stator 100 there are therefore no complete re-magnetizations during rotor movements, so that a high efficiency of the linear generator 10 can be expected ⁇ .
  • a stator 100 as described above can convert the power provided by the thermal process in an efficient manner as electrical energy, but it cannot start the R-FKLG 1 without auxiliary means, because no motor operation is possible with this arrangement, which could pull the rotor 121 and thus the piston 120 to the UT position.
  • the piston 121 In the case of a star ⁇ with aids, the piston 121 must be pushed into the UT position and then released. This can be done, for example, with mechanical tie rods and servo motors.
  • Another way to start is by filling the combustion chamber 1 10 with compressed air until the piston 120 has reached the UT position. The compressed air can either be generated and fed externally. Alternatively, a turbocharger can be used for this, which is equipped with an electric drive for the paddle wheels ⁇ a ⁇ e ⁇ .
  • the linear generator 10 can start the R-FKLG 1 without external help ⁇
  • the structure of the electrical machine must be adjusted ⁇ .
  • a structure consisting of several pole planes as in FIG. 13 with alternating magnetic polarities offers itself.
  • a stator 100 layered in this way can generate an axial force which is greater than the reluctance force ⁇ which also acts in the longitudinal direction. It is thus possible to catapult the piston 120 or rotor 121 for starting the R-FKLG 1 into the UT position by means of motor operation of the linear generator 10.
  • a disadvantage of this multilayer stator and rotor structure is that the rotor 121 must be structured into individual pole faces (see FIGS. 13 and 14).
  • the resulting pole faces of rotor 121 made of soft magnetic rotor materials must be completely magnetized several times when they are swept over stator 100. Therefore, lower efficiency levels in generator operation must be expected.
  • FIG. 14 Of particular interest in FIG. 14 is an arrangement with an inner and outer stator and the rotor 121 between the two stator modules.
  • two magnetically active air gaps 122 arise on the inner and outer surfaces of the rotor 121. Radial forces acting on rotor 121 can be minimized by this arrangement. The reluctance forces acting on the rotor also benefit from the two magnetically active air gaps 122.
  • Fig. 1 6 shows an electrical generator with axial flow guidance in the rotor. You can see the cylindrical rotor poles with soft magnetic material of different thickness (transformer or electrical sheet). The thickness of the rotor poles is selected so that a homogeneous flux density in the rotor poles is achieved with a minimal rotor weight ⁇ . 16 shows a configuration with 3 ring coils in the stator. At OT, for example, these can be connected and operated individually or in parallel on the rectifier. If the rotor speed slows down before UT is reached, the series connection of the coils that are still swept by the rotor is suitable for operation with the rectifier. This ensures that the electrical generator can be operated with optimum efficiency depending on the rotor speed.
  • FIG. 17 illustrates ⁇ the control electronics of a single stator coil.
  • a global controller (control logic) takes over the control of all stator coils 1000 at the same time, whereby not all coils 1000 always have to be controlled.
  • Electrical energy from the line generator 10 is temporarily stored in a battery. Energy from this battery can be used to start the FKLG 1.
  • the generator controller is designed, for example, as a switchable bridge rectifier (FIG. 18).
  • the rectifier is switched on or off with the signal “CNT” and the rotor is thus braked by drawing energy.
  • the switch-on cycles there are different possibilities for the switch-on cycles in order to control the energy consumption for the desired speed profile of the rotor 121.
  • the motor voltage Vsup can be applied to the stator coil 1000 using the control signals Cntl and Cn ⁇ 2 with both polarities.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)

Abstract

La présente invention concerne un procédé pour faire fonctionner un générateur linéaire à piston libre (1), pour produire de l'énergie électrique, ledit générateur linéaire à piston libre (1) comportant au moins un générateur linéaire (10) ainsi qu'au moins une unité de combustion (11) dotée d'au moins une chambre de combustion (110) et l'unité de combustion (11) et le générateur linéaire (10) étant couplés l'un à l'autre par l'intermédiaire d'au moins une unité piston-rotor (12), ladite unité piston-rotor (12) comportant au moins un rotor (121) ainsi qu'au moins un piston (120) qui présente une course d'expansion d'un point mort haut (OT) à un point mort bas (UT) et une course de compression du point mort bas (UT) vers le point mort haut (OT). Après l'accélération de l'au moins au piston (120), le prélèvement d'énergie électrique par le générateur linéaire (10) est réglé ou commandé de telle sorte qu'une allure de la vitesse de consigne du piston (120) soit contrôlée entre OT et UT est atteint au moins dans certaines zones, caractérisé en ce que l'énergie pour la réalisation de la course de compression est prélevée sur le générateur linéaire (10) qui fournit cette énergie pendant la course d'expansion dans le générateur linéaire (10) sous forme d'énergie stockée magnétiquement.
PCT/EP2019/068421 2018-07-13 2019-07-09 Procédé pour faire fonctionner un générateur linéaire à piston libre Ceased WO2020011790A1 (fr)

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DE102018117066.1A DE102018117066A1 (de) 2018-07-13 2018-07-13 Verfahren zum Betreiben eines Freikolbenlineargenerators
DEDE102018117066.1 2018-07-13

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114856840A (zh) * 2021-03-01 2022-08-05 傅强 全电控制自由活塞四冲程内燃发电系统
CN115163325A (zh) * 2021-04-02 2022-10-11 中国科学院理化技术研究所 回热式热功转换机械设备
US12173642B1 (en) * 2023-08-21 2024-12-24 Richard Kraus Free-piston linear generator

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112267939B (zh) * 2020-10-22 2021-11-05 聊城大学 基于振动加速度信号的fplg稳定运行控制方法及系统
CN116357402B (zh) * 2021-12-28 2025-08-12 宁波奥克斯电气有限公司 活塞式膨胀机和空调器

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10219549A1 (de) 2002-04-25 2003-12-04 Deutsch Zentr Luft & Raumfahrt Freikolben-Verbrennungsvorrichtung mit elektrischem Lineartrieb
DE102008030633A1 (de) * 2008-06-24 2009-12-31 Umc Universal Motor Corporation Gmbh Verfahren zum Betreiben einer Freikolbenvorrichtung
DE102008042169A1 (de) * 2008-09-17 2010-03-18 Robert Bosch Gmbh Freikolben-Verbrennungsmaschine
DE112012000915T5 (de) 2011-03-28 2013-11-14 Kabushiki Kaisha Toyota Chuo Kenkyusho Freikolbengenerator
US20150001852A1 (en) * 2012-01-19 2015-01-01 Libertine Fpe Ltd. Linear Electrical Machine
DE102014001770A1 (de) 2014-02-09 2015-08-13 Karl-Ulrich Stein Verbrennungskraftmaschine mit linearer elektrischer Führung
DE102016109029A1 (de) 2016-05-17 2017-11-23 Deutsches Zentrum für Luft- und Raumfahrt e.V. Freikolbenvorrichtung und Verfahren zum Betreiben einer Freikolbenvorrichtung
WO2017198569A1 (fr) * 2016-05-17 2017-11-23 Deutsches Zentrum für Luft- und Raumfahrt e.V. Dispositif à piston libre

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10219549A1 (de) 2002-04-25 2003-12-04 Deutsch Zentr Luft & Raumfahrt Freikolben-Verbrennungsvorrichtung mit elektrischem Lineartrieb
DE102008030633A1 (de) * 2008-06-24 2009-12-31 Umc Universal Motor Corporation Gmbh Verfahren zum Betreiben einer Freikolbenvorrichtung
DE102008042169A1 (de) * 2008-09-17 2010-03-18 Robert Bosch Gmbh Freikolben-Verbrennungsmaschine
DE112012000915T5 (de) 2011-03-28 2013-11-14 Kabushiki Kaisha Toyota Chuo Kenkyusho Freikolbengenerator
US20150001852A1 (en) * 2012-01-19 2015-01-01 Libertine Fpe Ltd. Linear Electrical Machine
DE102014001770A1 (de) 2014-02-09 2015-08-13 Karl-Ulrich Stein Verbrennungskraftmaschine mit linearer elektrischer Führung
DE102016109029A1 (de) 2016-05-17 2017-11-23 Deutsches Zentrum für Luft- und Raumfahrt e.V. Freikolbenvorrichtung und Verfahren zum Betreiben einer Freikolbenvorrichtung
WO2017198569A1 (fr) * 2016-05-17 2017-11-23 Deutsches Zentrum für Luft- und Raumfahrt e.V. Dispositif à piston libre

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114856840A (zh) * 2021-03-01 2022-08-05 傅强 全电控制自由活塞四冲程内燃发电系统
CN115163325A (zh) * 2021-04-02 2022-10-11 中国科学院理化技术研究所 回热式热功转换机械设备
US12173642B1 (en) * 2023-08-21 2024-12-24 Richard Kraus Free-piston linear generator

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