EP3921541B1 - Verfahren zum betreiben eines linearmotorverdichters sowie linearmotorverdichter - Google Patents

Verfahren zum betreiben eines linearmotorverdichters sowie linearmotorverdichter Download PDF

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Publication number
EP3921541B1
EP3921541B1 EP20705144.2A EP20705144A EP3921541B1 EP 3921541 B1 EP3921541 B1 EP 3921541B1 EP 20705144 A EP20705144 A EP 20705144A EP 3921541 B1 EP3921541 B1 EP 3921541B1
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EP
European Patent Office
Prior art keywords
linear motor
piston arrangement
point
during
piston
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.)
Active
Application number
EP20705144.2A
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German (de)
English (en)
French (fr)
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EP3921541A1 (de
Inventor
Adrian Luzi VALÄR
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Burckhardt Compression AG
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Burckhardt Compression AG
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Publication of EP3921541A1 publication Critical patent/EP3921541A1/de
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B19/00—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00
    • F04B19/003—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00 free-piston type pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/06—Control using electricity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/06—Control using electricity
    • F04B49/065—Control using electricity and making use of computers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2201/00—Pump parameters
    • F04B2201/02—Piston parameters
    • F04B2201/0201—Position of the piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2201/00—Pump parameters
    • F04B2201/02—Piston parameters
    • F04B2201/0202—Linear speed of the piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2201/00—Pump parameters
    • F04B2201/02—Piston parameters
    • F04B2201/0206—Length of piston stroke
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2203/00—Motor parameters
    • F04B2203/04—Motor parameters of linear electric motors

Definitions

  • the invention relates to a method for operating a linear motor compressor.
  • the invention further relates to a linear motor compressor.
  • the document US2018/0051690A1 discloses a free piston linear motor compressor in which the compressor is configured as a reciprocating compressor, the linear motor is configured in two poles, and the entire free piston linear motor compressor is operated at a resonant frequency.
  • This linear motor compressor is used to compress a gaseous process fluid, in particular natural gas.
  • This linear motor compressor is operated continuously and with a sinusoidal resonant frequency during the refueling of a natural gas vehicle.
  • the operating possibilities of this linear motor compressor are extremely limited and economically disadvantageous.
  • the object of the invention is to operate a linear motor compressor with a more advantageous operating method for compressing and/or expanding a gaseous process fluid.
  • the object is achieved in particular with a method for operating a linear motor compressor comprising an electric linear motor, a cylinder and a linearly movable free-piston arrangement with a piston, the cylinder and the piston forming a compression chamber, the free-piston arrangement being driven directly by the linear motor and along a stroke path between is moved back and forth between an upper dead center and a lower dead center, with a fluid being supplied to the compression chamber from the outside, with the supplied fluid being compressed or expanded in the compression chamber and then being discharged to the outside again, with at least one state variable being specified for the linear motor compressor , and wherein the linear motor is controlled in such a way that the linear motor compressor has the predetermined state variable.
  • a linear motor compressor comprising at least one electric linear motor, a cylinder and a linearly movable free-piston arrangement with at least one piston, the cylinder and the piston forming at least one compression chamber, the free-piston arrangement being driven directly by the linear motor, the compression chamber being an outlet valve and an inlet valve are fluidly connected to the outside, with a control device controlling the linear motor in such a way that the free-piston arrangement is moved back and forth with a predetermined state variable between a top dead center and a bottom dead center.
  • a relation between the stroke distance of the free-piston arrangement and its speed is preferably specified as a predetermined state variable, also referred to below as the speed-travel curve.
  • This speed-distance curve may comprise at least one point, a stroke distance and a predetermined, associated speed, and preferably comprises a plurality of points, each point comprising a point along the stroke path and a speed associated with this point.
  • a path setpoint curve to be maintained along at least a section of the entire lifting path, and preferably along the entire lifting path, i.e. a setpoint profile relating to the lifting path and setpoint speed, setpoint acceleration and/or setpoint force, is advantageously specified as the state variable.
  • a time setpoint curve to be maintained during a partial period of time or a section of the entire lifting path, and preferably a lifting time required during the duration of the entire lifting path, i.e. a setpoint profile relating to the setpoint speed, setpoint acceleration and/or setpoint force as a function of the lifting time, is specified as the state variable.
  • the linear motor compressor is advantageously operated with a control strategy in which the free-piston arrangement can be moved "freely” on the basis of the forces acting in the compression chamber and any additional frictional forces that are also acting, with the linear motor generating a controllable force can exert on the free-piston arrangement and thereby influences the free movement of the free-piston arrangement from the outside and preferably influences it in a predetermined manner.
  • the linear motor is given a speed profile or force profile as a function of displacement or as a function of time, with this force profile during operation of the Linear motor compressor can be modified by a control intervention to ensure that the free-piston arrangement has the predetermined state variable, or that the behavior of the free-piston arrangement approaches the predetermined state variable due to the control intervention.
  • the path-time dependency of the movement of the free-piston arrangement and thus the path-time dependency of the piston movement is not directly controlled, i.e. no predefined path-time curve is specified for the movement of the free-piston arrangement, but rather the movement curve of the Free-piston arrangement or the piston results as a consequence of the force profile used or resulting from the acting forces.
  • the specified state variable is thus ultimately achieved via the specification of a force profile.
  • the force profile used is adapted to the corresponding application and the corresponding operating method of the linear motor compressor.
  • the linear motor compressor can be operated as an application, for example as a compressor or as an expander of a gas.
  • the linear motor compressor is preferably operated to compress a gas.
  • the operating method or the force profile can be optimized, for example, so that the free-piston arrangement is moved relatively quickly during the compression phase of the gas, in particular at a higher average speed, and that the free-piston arrangement is moved at a reduced speed during the subsequent ejection phase of the gas. in particular, is moved at a lower average speed, which reduces the flow resistance when the gas flows out of the compression chamber.
  • the time constant for a complete cycle of compression but by going through the compression phase faster and going through the exhaust phase slower, the flow resistance of the gas during the outflow can be reduced, and with it the energy that is required is to push the gas out of the compression chamber.
  • the free-piston arrangement and thus the entire linear motor compressor can be operated in the most varied of ways, depending on the desired variable to be optimized.
  • the state variable can be selected, for example, in such a way that the maximum force to be delivered by the linear motor or the maximum power to be delivered by the linear motor is limited, or the energy required to operate the linear motor compressor is minimized by also supplying energy to the linear motor in sections during the cycle is withdrawn and fed back to the linear motor with a time delay.
  • the method according to the invention therefore has the advantage that the linear motor compressor can be operated with a large number of possible, predetermined state variables.
  • the linear motor compressor according to the invention can be operated in a wide variety of ways and in particular independently of movement sequences specified by a crankshaft by specifying a state variable such as the target speed, the target acceleration or the target force as a function of the stroke.
  • the operating method can be optimized for a size such as energy consumption, maximum linear motor power or maximum linear motor force, depending on the requirement.
  • the linear motor compressor may include a single compression chamber.
  • the linear motor compressor particularly advantageously comprises two compression chambers, a first and a second compression chamber.
  • the free-piston arrangement preferably has a piston on each of the two end faces spaced apart in the stroke direction, these two pistons being operated in opposite directions or in opposite directions by the free-piston arrangement, so that alternately in one compression chamber, for example the first compression chamber, a compression and then an ejection of a fluid, and in the other compression chamber, for example the second compression chamber, a relaxation and then a suction of the fluid takes place at the same time, and vice versa.
  • the linear motor or the free-piston arrangement particularly preferably has a stroke length in the range between 50 mm and 500 mm.
  • the linear motor has at least three actively controllable magnetic poles arranged one after the other in the stroke direction, and preferably between 5 and 50 actively controllable magnetic poles, and particularly advantageously between 10 and 20 controllable magnetic poles.
  • Such a number of actively controllable magnetic poles has the advantage that the force exerted by the linear motor on the free-piston arrangement during the movement along the stroke path can be controlled as a function of the stroke path or as a function of time by a corresponding selective excitation of the individual magnet poles or those connected in groups.
  • only positive electrical power is supplied to the linear motor to thereby drive the free piston assembly.
  • electrical power is discharged from the linear motor along at least a section of the entire stroke, so that the linear motor generates a braking effect within this section in order to brake the free-piston arrangement with the linear motor.
  • the braking effect or the output braking power can also be controlled as a function of the stroke distance.
  • the linear motor can therefore only be operated in a driving manner, or in a driving and braking manner, or in a combination of at least two of the properties in a driving, braking and neutral manner, with neutral being understood to mean that the linear motor causes neither a driving nor a braking force.
  • the electrical power drawn off by the linear motor is temporarily stored in an electrical storage device and then fed back to the linear motor with a time delay.
  • the linear motor compressor is preferably operated at a speed in the range operated between 200 to 1000 revolutions per minute or operated with a stroke frequency of 200 to 1000 periods or back and forth movements per minute.
  • a period of movement of the free piston assembly is one complete cycle of movement beginning from a starting point, passing through top dead center and bottom dead center of piston movement once.
  • a period of piston movement includes a compression phase in the compression chamber for the movement from bottom dead center to top dead center and then an exhaust phase, and then includes for the movement from top dead center to bottom dead center an expansion phase in the compression chamber and then an intake phase for the to promoting fluid.
  • the starting point is basically arbitrary. For example, the starting point is bottom dead center.
  • the free-piston arrangement is preferably moved back and forth between top dead center and bottom dead center at a predetermined speed-displacement curve.
  • the free-piston arrangement is preferably moved from a bottom dead center during a compression phase to the opening point of the outlet valve with a predetermined speed-displacement curve in such a way that the linear motor has to deliver a constant or essentially constant power. This results in the advantage that no high and possibly unpredictable current peaks occur during the electrical supply of the linear motor.
  • the free-piston arrangement is driven from bottom dead center during a compression phase to the opening point of the outlet valve and then during an exhaust phase to the closing point of the outlet valve with a predetermined speed-distance curve such that the mean speed during the compression phase is higher than during the Ejection phase and/or that the average speed during the expansion phase is higher than during the intake phase.
  • the predetermined speed-displacement curve or the predetermined speed-time curve of the free-piston arrangement has at least in the area of one of the switching points: opening of the outlet valve, closing of the outlet valve, opening of the inlet valve and closing of the inlet valve compared to the rest Speed-path course reduced speed, so that at reduced speed of the free-piston arrangement opening or closing outlet or inlet valve is moved at reduced speed.
  • the reduced speed of the opening or closing valve preferably results in reduced wear on the valve, which advantageously results in an increased service life or service life of the valve.
  • the compression chamber has an expansion phase between a closing point of the outlet valve and the opening point of the inlet valve, the linear motor being controlled in such a way that it actively drives the free-piston arrangement during the entire expansion phase.
  • the volume conveyed by the linear motor compressor is changed by changing the maximum stroke of the linear motor or the location of the top dead center and/or the location of the bottom dead center, so that the volume conveyed can be changed in the short or long term, e.g. is reduced or increased.
  • the free-piston arrangement is braked at least in sections during the to-and-fro movement between top dead center and bottom dead center by operating the linear motor as a generator.
  • the linear motor as a generator.
  • the released braking energy is converted into electrical energy and temporarily stored for later use.
  • the linearly movable piston arrangement is operated as an expander for a fluid, and the linear motor is operated as a generator at least during a partial section of a movement in the stroke direction X, in that the compression chamber of the linear motor compressor is now used as an expansion chamber, in that the expansion chamber is fed a lower volume via the outlet valve Pressurized fluid is supplied, the fluid is expanded in the compression chamber operated as an expansion chamber and is then ejected via the inlet valve, and by the free-piston arrangement of the linear motor operated as a generator moving backwards with a predetermined speed-path curve or a predetermined speed-time curve and is moved.
  • the opening and closing of the outlet valve and/or inlet valve is actively controlled as a function of the position of the free-piston arrangement.
  • the linear motor compressor advantageously comprises at least one electric linear motor, a cylinder and a linearly movable free-piston arrangement with at least one piston, with the cylinder and the piston forming at least one compression chamber, with the free-piston arrangement being driven directly by the linear motor, with the compression chamber containing fluid via an outlet valve and an inlet valve is conductively connected to the outside, with a control device controlling the linear motor in such a way that the free-piston arrangement is moved back and forth between a top dead center and a bottom dead center, preferably with a predetermined motor and/or generator power curve.
  • the linear motor compressor comprises a first and a second compression chamber, which are arranged in opposite directions with respect to the free-piston arrangement, so that they act in opposite directions.
  • the linear motor of the linear motor compressor can be operated as a motor and/or as a generator, with the control device controlling the linear motor in such a way that the free-piston arrangement has a predetermined speed-path curve or a predetermined speed-time curve when moving between a top dead center and a has bottom dead center.
  • the linear motor comprises at least three pole pairs, and preferably between 5 and 50 pole pairs distributed or mutually spaced in the longitudinal direction of the linear motor.
  • the linear motor compressor comprises at least one electric linear motor, a cylinder and a linearly movable free-piston arrangement with at least one piston, with the cylinder and the piston forming at least one compression chamber, with the free-piston arrangement being driven directly by the linear motor, with the compression chamber conducting fluid via an outlet valve and an inlet valve is connected to the outside, with a control device controlling the linear motor in such a way that the free-piston arrangement is moved back and forth between a top dead center and a bottom dead center with a predetermined state variable Z soll .
  • the linear motor compressor according to the invention has the advantage that in a preferred embodiment it has no moving parts, with the exception of the valves and the free-piston arrangement, which improves the service life and efficiency of the linear motor compressor and also reduces the manufacturing costs, installation and maintenance.
  • the linear motor compressor is preferably designed to be oil-free, which means that no oil is required for lubricating purposes.
  • the linear motor compressor according to the invention is particularly suitable for compressing gases such as natural gas, other hydrocarbons, hydrogen or air.
  • the linear motor compressor according to the invention is also suitable for expanding pressurized gases, it being possible, in particular, for the linear motor to be operated at least temporarily as a generator during expansion.
  • the linear motor compressor according to the invention also suitable for simultaneously compressing a gas and relaxing or expanding a gas by expanding a gas in one chamber of the linear motor compressor and simultaneously compressing a gas in the other chamber of the linear motor compressor.
  • a combination of the linear motor in a free-piston compressor enables the construction of a compact linear motor compressor. Due to the direct mechanical connection of the two systems, the static and dynamic behavior is coupled. Therefore, good performance and high efficiency of the linear motor compressor can preferably be achieved if the compressor and linear motor are designed in such a way that they work together optimally and are preferably operated in the range of a resonant frequency. Preferably under such operating conditions, the free-piston compressor can exploit its advantages to the full.
  • An advantage in addition to the compact design is the fact that the piston can be hermetically sealed against the outside in a relatively simple manner and therefore also inexpensively, because the two cylinders in which the two pistons are located can be designed cost-effectively sealed against the outside, what allows gases to be compressed when there are high demands on ambient conditions, since the linear motor compressor causes only very little or no leakage of the pumped gas.
  • the two cylinders and the stator of the linear motor advantageously form a gas-tight outer shell.
  • no crank mechanisms are required, as are required in conventional piston compressors. This eliminates parts that require lubrication and have mechanical energy conversion losses. Due to the possibility of dispensing with lubricants, the linear motor compressor according to the invention is also suitable for applications with high cleanliness requirements.
  • FIG 1 shows schematically a linear motor compressor 1 comprising a linear motor 14 and comprising a double-acting reciprocating compressor 15.
  • the reciprocating compressor 15 comprises a cylinder 2 in which a linearly movable piston 3 is arranged, which is connected directly to the linear motor 14 via a piston rod 9 and is directly driven by it.
  • Directly connected or directly driven is understood here to mean that no gear is arranged between the piston 3 and the linear motor 14, so that the force between the linear motor 14 and the piston 3 is transmitted directly and thus without a gear connected in between.
  • a flexible coupling could also be arranged between the piston 3 and the linear motor 14, which preferably allows an independent alignment of the piston 3 and the linear motor 14.
  • the cylinder interior 5 is divided by the piston 3 into a first compression chamber 5a and a second compression chamber 5b, with the first and second compression chambers 5a, 5b being operated in opposite directions during operation due to the geometric arrangement.
  • the first and the second compression chamber 5a, 5b are each connected to an exterior space outside the cylinder interior 5 via an inlet valve 7a, 7b and an outlet valve 6a, 6b in a fluid-conducting manner.
  • arranged fluid lines which forward the fluid to downstream devices or supply it to upstream devices.
  • the reciprocating compressor 15 is the associated, idealized pV diagram, also referred to as a pressure-volume diagram, shown that the pressure P of a reciprocating compressor 15 in the first Compression chamber 5a of compressed gas as a function of the volume of the first compression chamber 5a.
  • the first compression chamber 5a has a stroke volume V H , a suction volume Vs and a dead space volume V tot , with the volume V increasing toward the right.
  • the same diagram also shows the pressure P of the gas in the first compression chamber 5a as a function of the stroke X of the piston 3, the stroke X increasing positively towards the left in the diagram shown, so that the positive direction of the stroke X runs towards the left.
  • figure 1 shows the piston 3 in the first piston position 3a, in which the piston 3 is at bottom dead center X BDC , the gas in the first compression chamber 5a having a suction pressure Ps.
  • the course of the idealized pV diagram is briefly explained below. Starting from bottom dead center X BDC , the piston 3 is moved in the positive X-direction, with the inlet valve 7a ideally being automatically closed at the closing point A due to the increasing pressure in the first compression chamber 5a, and the gas in the first compression chamber 5a remaining a compression phase BA is compressed to an outlet pressure Pa, the outlet valve 6a being automatically opened at the outlet pressure Pa, that is to say ideally at the opening point B.
  • the piston 3 is moved towards the top dead center X TDC , so that the gas in the first compression chamber 5a is expelled via the outlet valve 6a until the piston 3 has reached the position of the top dead center X TDC , and the outlet valve 6a is ideally closed at the closing point C.
  • the piston 3 is moved in the direction of the bottom dead center X BDC , with the residual gas still in the first compression chamber 5a being expanded to a suction pressure Ps, so that the inlet valve 7a ideally opens automatically at the opening point D.
  • the inlet valves 7a, 7b and the outlet valves 6a, 6b open and close automatically.
  • the residual gas in the first compression chamber 5a is compressed along the line DC to a pressure Pa and the outlet valve 6 is opened in a controlled manner at point C, so that gas under pressure Pa again flows into the first compression chamber 5a.
  • the cyclic process described above is particularly advantageous in the direction of the successive points A, D, C and B operated with a double-acting reciprocating compressor 15 having a first and a second compression chamber 5a, 5b, as in figure 1 shown.
  • the cyclic process in the direction of the successive points A, D, C and B has the advantage that the linear motor 14 can be operated as a linear generator, so that mechanical energy can be converted into electrical energy by the described expansion of the gas.
  • the linear motor compressor 1 can thus be operated as required for compressing or expanding a fluid, or in a mixed operation with temporary compression and two-time expansion of the fluid, with the linear motor 15 being supplied with electrical energy depending on the operating mode or electrical energy is dissipated.
  • the linear motor compressor 1 can also be operated in such a way that a fluid in the first compression chamber 5a is compressed and a fluid in the second compression chamber 5b is expanded, so that the expansion energy released in the first compression chamber 5a is used to compress the fluid in the second compression chamber 5b located fluid can be used.
  • the linear motor compressor 1 can also be operated in reverse by compressing a fluid in the first compression chamber 5a and expanding it in the second compression chamber 5b to compress or expand as needed , or can be operated at idle without supplying electrical power.
  • the second compression chamber 5b could be dispensed with, so that the reciprocating compressor 15 has only a first compression chamber 5a but no second compression chamber 5b that can be operated in opposite directions.
  • FIGS. 2 to 4 show another embodiment of a linear motor compressor 1.
  • This linear motor compressor 1 includes a free-piston assembly 16, comprising a linear motor rotor 10 and a first piston 3 and a second piston 4.
  • a stator 8 together with the linear motor rotor 10 forms a linear permanent magnet synchronous motor 14.
  • the linear motor compressor 1 comprises a cylinder 2 with two cylinder interiors 5, a first compression chamber 5a being divided by a first cylinder 2a and the first Piston 3 is formed, and a second compression chamber 5 b is formed by a second cylinder 2 b and the second piston 4 .
  • the first compression chamber 5a is connected to the outside via a first outlet valve 6a and a first inlet valve 7a to conduct fluid.
  • the second compression chamber 5b is connected via a second outlet valve 6b and a second inlet valve 7b to conduct fluid to the outside.
  • the first and second compression chambers 5a, 5b are operated in opposite directions via the free piston arrangement 16.
  • Sealing rings and/or bearing rings are preferably also arranged on the first and second pistons 3, 4, for supporting the free-piston arrangement 16 within the linear motor compressor 1, and for sealing the pistons 3, 4 with respect to the compression chambers 5a, 5b, such rings being generally known and in figure 2 are not shown.
  • the pistons 3.4 could also be designed as labyrinth pistons, so that sealing rings can be dispensed with because the labyrinth structure on the surface of the piston 3.4 causes the sealing function.
  • FIG 3 shows a longitudinal section along the section line FF through the linear permanent magnet synchronous motor 14 comprising a stator 8 with laminated stator segments 8a, comprising a plurality of preferably individually controllable stator windings 12a, 12b, 12c, 12d, 12e, 12f for generating actively controllable magnetic poles 13a - 13f or magnetic fields, and comprising a linear motor rotor 10 with a plurality of permanent magnets 10a arranged spaced apart from one another in the longitudinal direction, the linear motor rotor 10 forming part of the piston rod 9 .
  • the piston rod 9 includes attachment sections 9a, with which the first and the second piston 3.4 is connected.
  • the linear permanent magnet synchronous motor 14 advantageously includes two radial bearings 11 for guiding the piston rod 9.
  • figure 4 shows a section along the section line EE through the linear permanent magnet synchronous motor 14, with a section through the stator segment 8 and the second stator winding 12b, and a section through the piston rod 9 and the permanent magnet 10a.
  • the linear motor 14 and thus also the driven pistons 3.4 advantageously have a maximum stroke X L in the range between 50 mm and 500 mm.
  • the linear motor 14 thus allows relatively long-stroke movements.
  • the linear motor 14 shown comprises six actively controllable magnetic poles 13a-13f, each pole being surrounded by a stator winding 12a-12f, with each stator winding 12a-12f preferably being individually controllable.
  • the linear motor 14 preferably has between three and ten actively controllable magnetic poles 13a-13f, or preferably between 10 to 50 actively controllable magnetic poles 13a-13f.
  • the number of actively controllable magnetic poles 13a - 13f depends in particular on the length of the maximum stroke X L .
  • the number of actively controllable magnetic poles 13a-13f can also influence how precisely the force exerted by the stator 8 on the linear motor rotor 10 can be controlled as a function of time or as a function of the stroke X.
  • figure 5 shows an example of characteristic curves 30 to 33 of a possible activation of a device as in figure 1 or in figure 2 illustrated linear motor 14, the illustrated characteristics show the case in which the linear motor 14 is not connected to the reciprocating compressor 15, but only alone and independently of the reciprocating compressor 15 is operated.
  • the characteristic curve 30 shows the stroke X of the linear motor 14 as a function of time t during a complete cycle from bottom dead center X UTP to top dead center X OTP and back.
  • Characteristic curve 31 shows the speed of linear motor rotor 10 as a function of time t, linear motor 14 being controlled in such a way that the speed of linear motor rotor 10 as a function of time increases linearly in section 31a, is constant in section 31b, and is constant in section 13c linearly decreases and is zero in section 13d, so that the linear motor rotor 10 is at a standstill.
  • the linear motor rotor 10 When the linear motor rotor 10 is at a standstill, it has, as can be seen from the characteristic curve 30, reached the top dead center X TDC .
  • the characteristic curve 32 shows the acceleration of the linear motor rotor 10 as a function of time t, the linear motor rotor 10 being accelerated in sections 32a and 32g with constant, positive acceleration, in sections 32c, 32e with constant negative acceleration being decelerated, and in sections 32b, 32d and 32f is moved without acceleration.
  • Characteristic curve 33 shows the force exerted by linear motor 14 on linear motor rotor 10 as a function of time t, with a constant acceleration force being present in section 33a, with a small constant force being present in section 33b to overcome the frictional forces present when linear motor rotor 10 is moved, and a negative force being applied in section 33c in order to bring the linear motor rotor 10 to a standstill at top dead center X TDC .
  • a standstill ie during section 33d, there is no acceleration.
  • the linear motor rotor 10 is then accelerated again in section 33e by a constant force, kept in motion by the small constant force acting in section 33f to overcome the applied frictional forces, and by the constant force acting in section 33g at bottom dead center X UTP up to Slowed down.
  • the linear motor 14 brakes the linear motor rotor 10, the energy released in the process being able to be converted into heat, the linear motor 14 preferably being operated as a generator during sections 33c and 33g, and the electrical energy released in the process in one Energy storage, is preferably temporarily stored in the control device.
  • the linear motor 14 can be controlled via a corresponding control in a variety of ways as a function of the time t or the stroke X, with preferably at least one of the characteristic curves of stroke, Speed, acceleration and motor power is specified as a function of time t, with the control device controlling the linear motor 14 in such a way that it moves at least approximately in accordance with the specified characteristic curve.
  • the figure 6 shows another example of a control of the linear motor 14.
  • the characteristic curve 34 shows the stroke X of the linear motor 14 as a function of the time t during a complete cycle.
  • the characteristic curve 35 shows the speed, the characteristic curve 36 the acceleration and the characteristic curve 37 the motor force of the linear motor 14 as a function of the time t.
  • the characteristic curve according to figure 6 shows a similar course as the characteristic curve according to figure 5 , where the timeline is in figure 6 is much shorter, ie the movement in figure 6 runs much faster, which can also be seen from the fact that the values for speed, acceleration and motor power in figure 6 compared to figure 5 are significantly higher.
  • the possibility of operating the linear motor 14 with a large number of different characteristic curves as a function of time results in the advantage that a reciprocating compressor 15 which is driven by such a linear motor 14 can be operated in a large number of ways.
  • the linear motor 14 is preferably operated in such a way that the linearly movable free-piston arrangement 16 is given at least one state variable Z set as a function of the time t or as a function of the stroke X, with the linear motor 14 being controlled in such a way that the free-piston arrangement 16 has the given state variable Z set exhibits or at least approximately occupies.
  • This Control method allows the operation of the linear motor compressor 1 to be optimized, for example, with regard to predeterminable key figures, for example by specifying the maximum force to be delivered by the linear motor 14, the maximum power required to operate the linear compressor 1, the maximum acceleration that occurs and/or the maximum speed that occurs. which must not be exceeded during operation.
  • the linear motor compressor 1 comprises an electric linear motor 14 and a reciprocating compressor 15 driven by this.
  • the overall dynamics of the movement of the linear motor compressor 1 is thus essentially determined by the dynamics of the linear motor 14 in combination with the dynamics of the reciprocating compressor 15 connected to the linear motor 14, where the overall dynamics are essentially determined by the acting inertial forces, by the electromagnetic forces caused by the linear motor 14, by the gas forces caused by the reciprocating compressor 15 or acting in the reciprocating compressor 15, and by the frictional forces caused by the movement of the piston and the linear motor 14.
  • the two pistons 3.4 are driven by the force produced by the linear motor 14 in a reciprocating motion running in the stroke direction X.
  • the first piston 3 moves back and forth in a positive stroke direction X in the range between the bottom dead center X BDC and the top dead center X TDC .
  • the second piston 4 moves in the opposite direction to the first piston 3 and, as in figure 2 shown, in a positive stroke direction X, in the area between the top dead center X OTP and the bottom dead center X UTP .
  • the movement analysis of the free piston arrangement 16 is only considered for the cycle of the first piston 3, which extends in the positive X direction from bottom dead center X UTP to top dead center X OTP and back to the bottom Dead center X UTP moved.
  • the equation for the driving force F LM to be applied by the linear motor 14 to move the free-piston arrangement 16 is as follows: m G ..
  • x f LM + f per ⁇ f Pl ⁇ f fr ⁇ f fl
  • m g is the total mass of the free piston assembly 16
  • x is the displacement or stroke of the free piston assembly
  • F pr and F pl are the forces generated by gas pressure in the right, second, and left, first compression chambers 5b, 5a, respectively act on the first and second pistons 3,
  • F fr and F fl are the frictional forces of the right, second piston 4 and the left, first piston 3, respectively.
  • the control device can be given a state variable Z setpoint, the control device controlling the linear motor 14 in such a way that the linear motor compressor 1 has the predetermined state variable Z setpoint at least approximately.
  • a stroke path point X 1 i.e. a defined point along the stroke X, and a setpoint speed v setpoint assigned to this stroke path point and/or a setpoint acceleration a setpoint and/or a setpoint force F setpoint of the free-piston arrangement 16 can be specified as the state variable Z setpoint .
  • a stroke path time T L1 could also be specified, ie a defined point in time within the overall cycle time T, with the bottom dead center X UTP preferably being used as a reference for the time measurement.
  • the state variable Z set can therefore be im
  • a stroke path instant T L1 and a setpoint speed v setpoint assigned to it and /or a setpoint acceleration a setpoint and/or a setpoint force F setpoint of the free-piston arrangement 16 are also specified. If, as in figure 9 shown, for example to ensure that the speed of the free-piston arrangement 16 is reduced in the area of points B and D, a state variable Z desired would suffice, which should have the speed v at the stroke path point X 1 and the speed -v at the stroke path point X 2 should pretends.
  • a setpoint acceleration a setpoint and/or a setpoint force F setpoint could also be specified at a lifting path point.
  • a progression of the state variable Z soll to be maintained along at least a partial section of the stroke path X, and preferably along the entire stroke path X L , is specified as the state variable Z des .
  • a progression of the state variable Z soll to be maintained during part of the overall cycle time T and preferably during the overall cycle time T is specified as the state variable Z des.
  • a speed-displacement curve between bottom dead center X BDC and top dead center X BDC and/or top dead center X TDC and bottom dead center X BDC is specified as the state variable Z soll , according to which the free-piston arrangement 16 during of the operation of the in figure 2 illustrated linear motor compressor 1 is reciprocated.
  • figure 7 shows an example of such an operating method of the linear motor compressor 1 comprising both the linear motor 14 and the reciprocating compressor 15.
  • figure 7 shows as the state variable Z soll speed-displacement curves G 1 , G 2 , G 3 , G 4 according to an operating method according to the invention, which is carried out with the aid of figure 2 is explained.
  • the diagram according to figure 7 shows on the left side, to the left of point A, the movement of the first piston 3, which, starting from point A, the bottom dead center X PTU , moves according to the course G 1 over the in figure 1 shown point B moves to point C, the top dead center X OTP , and the moves according to the curve G 2 via point D back to point A, the bottom dead center X PTU .
  • the diagram according to figure 7 shows on the right-hand side, to the right of point A , the speed-displacement curves G 3 , G 4 of the second piston 4 as the state variable Z.
  • the second piston 4 Since the second piston 4 is moved in the opposite direction to the first piston 3, the second piston 4 leads with respect to the first piston 3 moves in the opposite direction in that the second piston 4, starting from point C, the top dead center X OTP , moves according to the curve G 3 over the in figure 1 shown point D moves to point A, the bottom dead center X UTP , and according to the course G 4 via the point B back to point C, the top dead center X OTP , moves. Since the first and second pistons 3, 4 are firmly connected to one another and therefore have the same speed, with the exception of the different sign of the speed, the curves G 1 and G 3 otherwise have an identical curve. For the same reasons, curves G 2 and G 4 also show an identical curve, with the exception of the different sign of the speed.
  • the linear motor compressor 1 is moved between the bottom dead center X BDC and the top dead center X BDC and on the way back between the top dead center X BDC and the bottom dead center X BDC with the same state variable Z set or with the same speed- displacement curve, so that all Courses, with the exception of the different signs relating to speed, have the same course G 1 , G 2 , G 3 , G 4 .
  • the first piston 3 has a first average speed V m1 between points A and B, the compression phase AB, and the piston 3 has a second average speed V m2 between points B and C, the exhaust phase BC, wherein the first average speed V m1 is greater than the second average speed V m2 .
  • the average speed is understood to mean the average speed value of the piston 3 or 4 between two points.
  • the first average speed V m1 thus corresponds to the average speed between points A and B, or the first average speed V m1 corresponds to the time integral of the speed V(t) between points A and B, divided by the time required for movement of the piston 3 between the points A and B is required, or corresponds the first mean velocity V m1 is the integral of the velocity V(X) along the path X between points A and B divided by the distance AB required to move the piston 3 between points A and B.
  • the second average speed V m2 thus corresponds to the average speed between points B and C, or the second average speed V m2 corresponds to the integral of the speed V(t) or V(X) between points B and C, divided by the time or the distance BC, which is required to move the piston 3 between the points B and C.
  • the first piston 3, during the return movement from point C to point A, between points C and D, the relaxation phase CD, has a third mean speed V m3 , and the piston 3 has between points D and A, the Intake phase DA, a fourth average speed V m4 , the third average speed V m3 being greater than the fourth average speed V m4 .
  • the third average speed V m3 thus corresponds to the average speed between points C and D, or the third average speed V m3 corresponds to the integral of the speed V(t) or V(X) between points C and D, divided by the Time or the distance CD, which is required to move the piston 3 between the points C and D.
  • the fourth average speed V m4 thus corresponds to the average speed between points D and A, or the fourth average speed V m4 corresponds to the integral of the speed V(t) or V(X) between points D and A, divided by the time or the distance DA, which is required to move the piston 3 between the points D and A.
  • the linear motor compressor 1 is preferably operated in such a way that the pistons 3 and 4 are controlled according to their reciprocation, apart from that on the axes figure 7 required reflections, identical speed-path curves G 1 and G 4 , or identical Have speed-path curves G 2 and G 3 .
  • the two pistons 3 and 4 it is also possible for the two pistons 3 and 4 to have a different speed path profile when moving back and forth, for example a different, different speed path profile when they move from right to left than moving from left to right.
  • the interaction of the linear motor 14 and the reciprocating compressor 15 can also be understood in the speed-displacement curve G 1 shown.
  • curve G 1 has a relatively rapid increase, which is due in particular to the fact that small forces are still required in reciprocating compressor 15 at the start of the compression phase.
  • the second compression chamber 5b or the gas located therein is in a relaxation phase, so that this gas drives the second piston 4, so that the combination of the driving force of the linear motor 14 and the relaxation force acting on the second piston 4 allows rapid movement, ie a increasing speed V or an acceleration of the free-piston arrangement 16 result.
  • the free-piston arrangement 16 is driven by the linear motor 14 so quickly that the relaxation force makes a negligibly small contribution or no contribution at all to the movement of the free-piston arrangement 16 .
  • the compression power consumed by the reciprocating compressor 15 increases constantly, so that the speed of the free-piston arrangement 16 is reduced, which applies in particular when the linear motor 14 is operated with constant power.
  • the outlet valve 6a is opened, with the speed of the free-piston arrangement 16 continuing to decrease due to the flow resistance occurring at the outlet valve 6a.
  • the free piston assembly 16 must be braked and brought to a standstill up to the top dead center X OTP , which is preferably done in that the linear motor 14 generates a braking force and is advantageously operated as a generator, wherein the electrical energy generated is preferably temporarily stored in a control device, for example in order to accelerate the free-piston arrangement 16 again in section AX 3 .
  • the figure 7 shows a speed-displacement diagram (vx diagram) as the state variable Z desired .
  • vx diagram speed-displacement diagram
  • one of the Figures 5 or 6 characteristic curves 30 to 37 shown are specified, for example stroke, speed, acceleration or force as a function of time.
  • the free-piston arrangement 16 is moved, starting from bottom dead center X BDC during a compression phase AB, to the opening point B of the outlet valve 6, with a predetermined speed-displacement curve G 1 in such a way that the linear motor 14 has a constant or essentially constant performance has to deliver.
  • the power is calculated from the drive force F LM to be applied by the linear motor 14 multiplied by the speed V of the free-piston arrangement 16. With a given constant power, the predetermined speed-displacement curve G 1 can thus be calculated.
  • This method has the advantage that the linear motor compressor can also be operated safely with lower power.
  • the linear motor 14 can be operated as a generator, at least along part of the relaxation phase CD, in that the linear motor 14 is driven by the relaxation forces Caused movement of the piston 3.4 slows down by a generator operation, wherein the electrical energy generated is preferably temporarily stored.
  • the linear motor 14 is actuated along at least a partial section of the relaxation phase CD and preferably during the entire relaxation phase CD in such a way that the linear motor 14 does not have an active braking effect on the free-piston arrangement 16 during the entire relaxation phase CD, preferably in such a way that the Linear motor 14 during the entire relaxation phase CD and preferably during points C and A, ie the entire phase CA exert a positive force acting in the direction of bottom dead center X UTP on the free-piston arrangement 16 .
  • This method ensures that the energy released by the gas in the dead space V tot during the expansion during the expansion phase CD is preferably completely converted into kinetic energy of the free piston arrangement 16, which supports compression of the gas in the second compression chamber 5b , in that the kinetic energy of the free-piston arrangement 16 is transferred to the gas via the second piston 4 .
  • figure 8 shows another advantageous operating method of the in figure 2 illustrated linear motor compressor 1.
  • figure 8 shows a rather schematic, ie slightly idealized, speed-path diagram of the first piston 3, the diagram showing the speed of the first piston 3 as a function of the stroke X during phase AC for a simplified illustration of the ongoing process, and the diagram subsequently to the right shows the speed of the first piston 3 as a function of the stroke X during the phase CA, the stroke X during the phase CA being shown running to the right for better illustration, in contrast to FIG figure 7 .
  • the first piston 3 is located both at the beginning and at the end of the in figure 8 illustrated diagram at bottom dead center X UTP .
  • the curves G 1 and G 2 for the free-piston arrangement 16 are specified as the predetermined state variable Z set , namely speed-displacement curves as in FIG figure 8 shown.
  • the compression phase AB is relatively high speed, in particular with a relatively high first mean speed V m1 , and thus run through relatively quickly in terms of time.
  • the speed v is reduced, so that the free-piston arrangement 16 is moved during the exhaust phase BC at a reduced speed, or at a lower compared to the compression phase AB second average speed V m2 .
  • the free-piston arrangement 16 is operated with a predetermined state variable Z set , a predetermined speed-displacement curve or a predetermined speed-time curve, that the first average speed V m1 during the compression phase AB is higher than the second average speed V m2 during the exhaust phase BC and/or that the duration of the compression phase AB is shorter than the duration of the exhaust phase B.C.
  • This method has the particular advantage that it is possible to increase the duration of the ejection phase BC.
  • This method has the advantage that the free-piston arrangement 16 can be operated at reduced speed during the exhaust phase BC, i.e. during the outflow of the gas from the exhaust valve 6a, which reduces the outflow resistance caused by the exhaust valve 6a, and thus also the outflow caused loss of energy reduced. Since there is no outflow during the compression phase AB, the compression phase AB can be run through without or with extremely little additional energy at an increased speed or at a higher average speed, so that the ejection phase BC can preferably be extended in time by the ejection phase BC compared to the compression phase AB lower average speed is passed through. This method has the advantage that the energy loss caused by the gas flowing out via the outlet valve can be reduced.
  • the first average speed V m1 during the compression phase AB high, preferably as high as possible
  • the second mean speed V m2 is set lower than the first mean speed V m1 , preferably as low as possible, but such that the given cycle time Tz of a complete reciprocating movement is maintained.
  • the duration of the exhaust phase BC can be extended or the outflow speed of the gas from the cylinder interior at the exhaust valve 6a can be reduced, which reduces the energy loss occurring at the exhaust valve. This method makes it possible to increase the efficiency of the linear motor compressor.
  • the linear motor 8 drives the free-piston arrangement 16 at least during a section of the compression phase AB, with the linear motor 8 braking the free-piston arrangement 16 at least during a section of the ejection phase BC, and is preferably operated as a generator which releases electrical energy , which is preferably temporarily stored and preferably reused to feed the linear motor 8 with electrical energy during the compression phase AB.
  • This short-term intermediate storage of electrical energy allows the linear motor compressor to be operated particularly efficiently and in particular to ensure that the first average speed V m1 during the compression phase AB is higher than the second average speed V m2 during the ejection phase BC.
  • the state variable Z desired according to curve G 2 shows the movement of free-piston arrangement 16 during phase CA, or the movement of first piston 3 from top dead center X TDC to bottom dead center X BDC .
  • the linear motor compressor 1 has a first and a compression chamber 5a, 5b which, as in figure 2 shown, are compressed by counter-rotating pistons 3.4, the two curves G 1 , G 2 have the same curve, with the exception of the sign of the speed v, as in FIG figure 8 shown.
  • the linear motor compressor 1 has only a single, first compression chamber 5a, the two courses G 1 and G 2 can also have a different course.
  • the mean speed V m3 of the relaxation phase CD is as in figure 8 shown higher than the average speed V m4 of the intake phase DA.
  • figure 9 shows another operating procedure of the in figure 2 illustrated linear motor compressor 1.
  • figure 9 shows a speed- displacement diagram of the first piston 3.
  • the curves G 1 and G 2 for the free-piston arrangement 16 are specified as the predetermined state variable Z set . These curves G 1 and G 2 are selected in such a way that the first and second piston 3.4 moves in the area of points A, B, C and D at a low or reduced speed v, with the speed at points C and A is reduced to 0 m/s, since the free-piston arrangement briefly comes to a standstill at this reversal point.
  • the speed in the area of points C and A ie in particular immediately before points C and A are reached, is preferably reduced particularly sharply, so that this speed is lower than at points B and D
  • Figures 9a and 9b show the speed of figure 9 in the area of point C or A in detail.
  • the speed at points C and A is very low, for example less than 0.1 m/s.
  • the reduced speed at points C and A means that the inlet valve 7a or the outlet valve 6a is closed at low speed, with the result that these valves are mechanically only slightly stressed by this gentle closing, so that the valves during can be operated reliably and preferably maintenance-free for a long time.
  • the free-piston arrangement 16 is braked towards the end of the stroke, towards the bottom dead center X BDC , first with a greater negative acceleration and then with a reduced negative acceleration, with the free-piston arrangement 16 at the dead center X BDC with reduced negative acceleration to a standstill decelerated and then accelerated again in the opposite direction.
  • the free-piston arrangement 16 is braked towards the end of the stroke, towards top dead center X TDC , first with a greater negative acceleration and then with a reduced negative acceleration, with the free-piston arrangement 16 is braked to a standstill at top dead center X TDC with reduced negative acceleration, and is then accelerated again in the opposite direction.
  • a state variable Z setpoint can only consist of a single point, for example as in figure 9 shown the Hubweg Vietnamese X 1 with the value v set.
  • the control is thus carried out in such a way that the free-piston arrangement 16 has the speed v set at the stroke path point X 1 . This ensures that the speed of the free-piston arrangement 16 has the desired , low speed v set at the stroke path point X 1 .
  • figure 10 shows a control device 20 for operating a linear motor compressor 1.
  • a control device 27 uses at least one sensor 21 to detect an actual state variable 29a via a signal line, at least one actual state variable of the linear motor compressor 1, preferably the stroke X and/or the speed v and/or the Acceleration and/or the acting force F of the free-piston arrangement 16.
  • the setpoint value of a state variable Z setpoint is specified via a setpoint specification device.
  • the control device 27 calculates a control signal 29b from the actual state variable 29a and the target state variable Z desired 29e, which is fed to an inverter control device 26.
  • the inverter control device 26 controls a power supply 23 and an inverter 22 via control lines 29c, 29d, the inverter 22 comprising a plurality of controls in order to connect a plurality of stator windings 12a, 12b, 12c, 12d via electrical conductors 24a, 24b, 24c, 24d to be controlled individually.
  • the power supply 23 is connected to the inverter 22 via a power line 25 .
  • the energy supply 23 includes an energy store, with the inverter 22 being controllable in such a way that electrical energy can be drawn from the linear motor compressor 1 and fed via the inverter 22 to the energy supply 23, in which the electrical energy is stored, preferably for a short time , for a period of preferably less than one second or less than one minute.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Computer Hardware Design (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Electromagnetic Pumps, Or The Like (AREA)
EP20705144.2A 2019-02-05 2020-02-05 Verfahren zum betreiben eines linearmotorverdichters sowie linearmotorverdichter Active EP3921541B1 (de)

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PCT/EP2020/052913 WO2020161210A1 (de) 2019-02-05 2020-02-05 Verfahren zum betreiben eines linearmotorverdichters sowie linearmotorverdichter

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NZ515578A (en) * 2001-11-20 2004-03-26 Fisher & Paykel Appliances Ltd Reduction of power to free piston linear motor to reduce piston overshoot
US7456592B2 (en) * 2003-12-17 2008-11-25 Lg Electronics Inc. Apparatus and method for controlling operation of reciprocating compressor
DE102007034293A1 (de) * 2007-07-24 2009-01-29 BSH Bosch und Siemens Hausgeräte GmbH Hubgeregelter Linearverdichter
JP5739420B2 (ja) * 2009-07-23 2015-06-24 ブルクハルト コンプレッション アーゲー 送出量を制御する方法および送出量制御機能を備える往復動圧縮機
US11466678B2 (en) 2013-11-07 2022-10-11 Gas Technology Institute Free piston linear motor compressor and associated systems of operation
CN107061249B (zh) * 2017-03-24 2020-07-07 青岛海尔智能技术研发有限公司 基于上死点控制的直线压缩机气缸容积调节方法

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