EP3921541A1 - Procédé pour faire fonctionner un compresseur à moteur linéaire, et compresseur à moteur linéaire - Google Patents

Procédé pour faire fonctionner un compresseur à moteur linéaire, et compresseur à moteur linéaire

Info

Publication number
EP3921541A1
EP3921541A1 EP20705144.2A EP20705144A EP3921541A1 EP 3921541 A1 EP3921541 A1 EP 3921541A1 EP 20705144 A EP20705144 A EP 20705144A EP 3921541 A1 EP3921541 A1 EP 3921541A1
Authority
EP
European Patent Office
Prior art keywords
linear motor
speed
dead center
free piston
during
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.)
Granted
Application number
EP20705144.2A
Other languages
German (de)
English (en)
Other versions
EP3921541B1 (fr
Inventor
Adrian Luzi VALÄR
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Burckhardt Compression AG
Original Assignee
Burckhardt Compression AG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Burckhardt Compression AG filed Critical Burckhardt Compression AG
Publication of EP3921541A1 publication Critical patent/EP3921541A1/fr
Application granted granted Critical
Publication of EP3921541B1 publication Critical patent/EP3921541B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
  • the invention further relates to a
  • Reciprocating compressor is designed, wherein the linear motor is designed with two poles, and wherein the entire free-piston linear motor compressor is operated at a resonance 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 resonance frequency while a natural gas vehicle is being refueled. The operating possibilities of this linear motor compressor are extremely limited and economically disadvantageous.
  • the object of the invention is a linear motor compressor with a
  • Claim 1 solved.
  • the dependent claims 2 to 18 relate to further advantageous method steps.
  • the object is further achieved with a linear motor compressor having the features of claim 19.
  • the dependent claims 20 and 21 relate to further advantageous ones
  • 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 directly from the linear motor
  • a fluid is supplied to the compression chamber from the outside, the fluid supplied being compressed or expanded in the compression chamber and then released back to the outside, the
  • Linear motor compressor at least one state variable is specified, and wherein the linear motor is controlled in such a way that the
  • Linear motor compressor has the specified 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 directly from the linear motor
  • the compression chamber is driven, wherein the compression chamber is fluidly connected to the outside via an outlet valve and an inlet valve, wherein a
  • Control device controlled the linear motor in such a way that the
  • Free piston assembly is moved back and forth with a predetermined state variable between a top dead center and a bottom dead center.
  • At least one stroke path point along the stroke or at least one stroke path time and one associated therewith is assigned as the state variable Target speed or a target acceleration or a target force
  • a relationship between the stroke path of the free piston arrangement and its speed is preferably specified as a predetermined state variable, hereinafter also referred to as the speed-path curve.
  • This speed-path curve can include at least one point, a stroke path and a predetermined, assigned speed, and preferably comprises a plurality of points, with each point having a point along the stroke path and one assigned to this point
  • Partial section of the entire stroke path and preferably a path-setpoint curve to be maintained along the entire stroke path, that is to say a
  • a stroke time required during a part-time duration or a partial section of the entire stroke path and preferably a stroke time required during the period of the entire stroke path
  • Time-setpoint curve to be observed that is to say pertaining to a setpoint profile
  • the linear motor compressor is advantageously operated with a control strategy in which the free piston arrangement changes due to the forces acting in the compression chamber
  • the linear motor is a
  • this force profile during the operation of the Linear motor compressor can be modified by a control intervention to ensure that the free piston arrangement has the specified state variable, or that the behavior of the
  • Free piston arrangement approximates the predetermined state variable due to the control intervention.
  • the path-time dependency of the movement of the free piston assembly and thus the path-time dependency of the piston movement is not controlled directly, that is, there is no predetermined path-time curve for the movement of the free piston assembly, but the movement curve of the The free-piston arrangement or the piston results as a consequence of the force profile used or resulting from the forces acting.
  • the predefined state variable is ultimately achieved by specifying a force profile.
  • the force profile used is particularly 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. When used as a compressor, it can
  • Compression phase of the gas is moved relatively quickly, in particular at a higher average speed, and that the free piston assembly is moved during the subsequent discharge phase of the gas at a reduced speed, in particular at a lower average speed, which reduces the flow resistance when the gas flows out of the compression chamber. It is thus possible, for example, to keep the time constant for a complete cycle of compression, but by running through the compression phase more quickly and the discharge phase more slowly, the flow resistance of the gas when it flows out can be reduced, and thus also 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 size to be optimized.
  • the state variable can be selected, for example, in such a way that the maximum force to be output by the linear motor or the maximum power to be output by the linear motor is limited, or the energy required to operate the linear motor compressor is minimized by adding energy to the linear motor in sections during the cycle is withdrawn and delayed again
  • Linear motor is fed.
  • 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.
  • Piston drive is driven via a cross head, has the disadvantage that the movement of the piston is rigidly coupled to the speed of the crankshaft, and that the speed of the piston is determined as a function of the angle of rotation of the crankshaft in particular by the geometric arrangement of the crankshaft and cross head .
  • the linear motor compressor according to the invention can be operated in a wide variety of ways and in particular independently of motion sequences predetermined by a crankshaft by appropriately 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 depending on requirements, can be reduced to a size such as energy consumption, maximum linear motor power or maximum
  • Linear motor power can be optimized.
  • the linear motor compressor can include a single compression chamber.
  • the linear motor compressor particularly advantageously comprises two
  • 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 a
  • 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 to 50 actively controllable magnetic poles, and particularly advantageously between 10 and 20 controllable magnetic poles. Such a number of actively controllable
  • switched magnetic poles is controllable.
  • the braking effect or the braking power output can also be controlled as a function of the stroke.
  • the linear motor can thus only be driving, or driving and braking, or in a combination of at least two of the
  • the electrical power dissipated by the linear motor is temporarily stored in an electrical memory and then fed back to the linear motor with a time delay. This enables particularly energy-efficient operation of the linear motor compressor according to the invention.
  • the linear motor compressor is preferably running at a speed in the range operated between 200 to 1000 revolutions per minute or with a stroke frequency of 200 to 1000 periods or back and forth
  • a period of the movement of the free piston arrangement is a complete cycle of a movement beginning from a starting point, the top dead center and the bottom dead center of the piston movement being passed through once.
  • a period of a piston movement comprises a compression phase in the for the movement from bottom dead center to top dead center
  • Compression chamber and then an exhaust phase includes the movement from top dead center to bottom
  • the starting point is basically arbitrary.
  • the starting point is bottom dead center.
  • the free piston arrangement is preferably with a predetermined
  • the free piston arrangement is moved with a predetermined speed-displacement curve in such a way that the linear motor has to deliver a constant or essentially constant power.
  • the free piston arrangement is driven with a predetermined speed-displacement curve in such a way that the mean speed during the
  • Compression phase is higher than during the exhaust phase and / or that the mean speed during the relaxation phase is higher than during the suction phase.
  • the predetermined speed-path curve or the predetermined speed-time curve has the
  • Free piston arrangement at least in the area of one of the switching points: opening the outlet valve, closing the outlet valve, opening the
  • the inlet valve and the closing of the inlet valve have a reduced speed compared to the rest of the speed-path curve, so that the outlet or inlet valve that opens or closes at a reduced speed of the free piston arrangement is moved at a reduced speed.
  • the reduced speed of the opening or closing valve preferably results in reduced wear on the valve, which advantageously results in a longer service life or service life of the valve.
  • the compression chamber has between a closing point of the outlet valve and the opening point of the
  • 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 conveyed volume can be changed for a short or long term, e.g. is reduced or increased.
  • the free piston arrangement is braked at least in sections during the back and forth movement between the top dead center and the bottom dead center by operating the linear motor as a generator. This makes it a particularly fast one
  • 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 by opening the expansion chamber via the outlet valve Pressurized fluid is supplied, the fluid is expanded in the compression chamber operated as an expansion chamber, and is then expelled via the inlet valve, and by the free piston arrangement of the linear motor operated as a generator with a predetermined speed-path profile or a predetermined speed-time profile. 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 one
  • Free piston arrangement with at least one piston, wherein the cylinder and the piston form at least one compression chamber, the
  • Free piston arrangement is driven directly by the linear motor, the compression chamber being fluidly connected to the outside via an outlet valve and an inlet valve, a control device controlling the linear motor in such a way that the free piston arrangement preferably has a predetermined motor and / or generator power curve between a top dead center and a bottom dead center is moved back and forth.
  • the linear motor compressor advantageously comprises a first and a second compression chamber, which with respect to the free piston arrangement
  • the linear motor of the linear motor compressor can advantageously be operated as a motor and / or as a generator, the control device being the
  • the linear motor comprises at least three pole pairs, and preferably between 5 and 50 distributed in the longitudinal direction of the linear motor or mutually
  • the linear motor compressor comprises at least one electric linear motor, a cylinder and a linearly movable free piston arrangement
  • 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 via a
  • the outlet valve and an inlet valve are fluidly connected to the outside, 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 soii .
  • the linear motor compressor according to the invention has the advantage that, in a preferred embodiment, with the exception of the valves and the free piston arrangement, it has no moving parts, which improves the service life and efficiency of the linear motor compressor, and also reduces manufacturing costs, installation and maintenance.
  • the linear motor compressor is preferably designed to be oil-free, which means that no oil is required for lubrication purposes.
  • the linear motor compressor is particularly suitable for compressing gases such as natural gas, other hydrocarbons, hydrogen or air.
  • gases such as natural gas, other hydrocarbons, hydrogen or air.
  • linear motor compressor according to the invention is also suitable for expanding pressurized gases, in particular when
  • the linear motor compressor according to the invention also suitable to compress a gas and to relax or expand a gas at the same time by releasing a gas in one chamber of the linear motor compressor and at the same time in the other chamber of the
  • Linear motor compressor a gas is compressed.
  • 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, this is static and
  • the linear motor compressor can preferably be achieved if the compressor and linear motor are designed in such a way that they cooperate optimally and are preferably operated in the range of a resonant frequency.
  • the free piston compressor can fully exploit its advantages.
  • An advantage in addition to the compact design is the fact that the piston can be hermetically sealed from 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 in a cost-effective manner tight against the outside, which a compression of gases with high demands on ambient conditions enables, since the linear motor compressor only an extremely small or no leakage of the conveyed gas occurs.
  • the two cylinders and the stator of the linear motor advantageously form a gas-tight outer shell.
  • FIG. 1 schematically shows a linear motor compressor and the associated pressure-volume diagram
  • FIG. 3 schematically shows a longitudinal section along the section line F-F through the linear motor of the linear motor compressor according to FIG. 2;
  • FIG. 4 schematically shows a cross section along the section line E-E through the linear motor of the linear motor compressor according to FIG. 3;
  • Linear motor compressor showing stroke, speed,
  • Fig. 7 is a speed-displacement diagram of the two pistons of the
  • FIG. 10 shows a control device for a linear motor compressor according to FIG.
  • Figure 1 shows schematically a linear motor compressor 1 comprising a
  • Linear motor 14 as well as comprising a double-acting reciprocating compressor 15.
  • the reciprocating piston compressor 15 comprises a cylinder 2 in which a linearly movable piston 3 is arranged, which is directly connected to the linear motor 14 via a piston rod 9 and is driven directly by the latter. Directly connected or directly driven is understood here to mean that there is no transmission between the piston 3 and the linear motor 14
  • Linear motor 14 can also have a flexible coupling, which preferably allows the piston 3 and linear motor 14 to be aligned independently.
  • the cylinder interior 5 is divided by the piston 3 into a first compression chamber 5a and a second compression chamber 5b, the first and second compression chambers 5a, 5b being operated in opposite directions during operation due to the geometric arrangement.
  • the first and second compression chambers 5a, 5b are each connected in a fluid-conducting manner via an inlet valve 7a, 7b and an outlet valve 6a, 6b to an outer space outside the cylinder interior 5.
  • fluid lines arranged, which forward the fluid to downstream devices or upstream
  • FIG. 1 shows three exemplary positions of the piston 3, a first
  • the associated, idealized pV diagram also referred to as a pressure-volume diagram, is shown, which shows the pressure P of the reciprocating compressor 15 in the first Compression chamber 5a shows compressed gas as a function of the volume of the first compression chamber 5a.
  • the first compression chamber 5a has a stroke volume VH, a suction volume Vs and a dead space volume V tot , the volume V increasing towards the right.
  • the same diagram also shows the pressure P of the gas in the first compression chamber 5a in FIG.
  • Figure 1 shows the piston 3 in the first piston position 3a, in which the piston 3 is in the lower
  • Dead center XUTP is located, wherein the gas in the first compression chamber 5a has a suction pressure Ps. The following is the course of the
  • Compression phase BA is compressed to an outlet pressure Pa, the outlet valve 6a at outlet pressure Pa, that is to say idealized at
  • Opening point B opens automatically.
  • the piston 3 is moved to the top dead center XOTP so that the gas in the first compression chamber 5a is expelled through the outlet valve 6a until the piston 3 has reached the top dead center XOTP position, and the outlet valve 6a is idealized closed at the closing point C.
  • Residual gas located in the compression chamber 5a is expanded to a suction pressure Ps, so that the inlet valve 7a is automatically opened at the opening point D, idealized.
  • gas is sucked into the first compression chamber 5a via the inlet valve 7a until the piston 3 has reached bottom dead center XUTP, and that
  • Inlet valve 7a is idealized at closing point A is closed.
  • the term idealized in connection with the points A, B, C and D expresses that these points in real operation, conditioned for example by Existing frictions of the valves are not exactly at the positions indicated in FIG. 1 but in a close area around the points.
  • the inlet valves 7a, 7b and the outlet valves 6a, 6b open and close automatically.
  • Compression chamber 5a, 5b operated as shown in FIG. Of the
  • the cycle 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 depending on requirements for compressing or relaxing a fluid, or in a mixed mode with temporary compression and two-way decompression of the fluid, with the linear motor 15 being supplied with electrical energy or electrical energy depending on the operating mode Energy is dissipated.
  • the linear motor compressor 1 can also be operated in such a way that one fluid in each case is in the first
  • Compression chamber 5a compressed and a fluid in the second
  • Compression chamber 5b is relaxed, so that in the first
  • Compression chamber 5a released relaxation energy can be used to compress the fluid located in the second compression chamber 5b.
  • 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, as required for compression or for decompression.
  • the linear motor 15 can be supplied with electrical energy or removed depending on the operating mode , or can be operated in idle mode without supplying electrical energy.
  • the second compression chamber 5b could be dispensed with, so that the reciprocating compressor 15 only has a first compression chamber 5a but no second compression chamber 5b that can be operated in opposite directions.
  • Figures 2 to 4 show a further embodiment of a
  • 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, with a first compression chamber 5a by a first cylinder 2a and the first Piston 3 is formed, and wherein a second compression chamber 5b is formed by a second cylinder 2b and the second piston 4.
  • the first compression chamber 5a is connected via a first outlet valve 6a and a first inlet valve 7a to conduct fluid to the outside.
  • 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 also preferably arranged on the first and second pistons 3, 4 for mounting the free piston arrangement 16 within the
  • Linear motor compressor 1 as well as for sealing the pistons 3, 4 with respect to the compression chambers 5a, 5b, such rings being generally known and not shown in FIG.
  • the piston 3.4 could also as
  • Labyrinth piston be designed so that sealing rings can be dispensed with because the labyrinth structure on the surface of the piston 3, 4 effects the sealing function.
  • Figure 3 shows a longitudinal section along the line F-F 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
  • Linear motor rotor 10 with a plurality of mutually spaced apart permanent magnets 10a in the longitudinal direction, wherein the
  • Linear motor rotor 10 forms part of the piston rod 9.
  • the piston rod 9 comprises fastening sections 9a to which the first and the second piston 3, 4 are connected.
  • the linear permanent magnet synchronous motor 14 advantageously comprises 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
  • the linear motor 14 and thus also the driven pistons 3, 4 advantageously have a maximum stroke XL in the range between 50 mm to 500 mm.
  • Linear motor 14 thus allows relatively long-stroke movements.
  • the linear motor 14 shown in FIGS. 2 to 4 comprises six actively controllable magnetic poles 13a-13f, each pole being surrounded by a stator winding 12a-12f, 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 is particularly dependent on the length of the maximum stroke XL.
  • the number of actively controllable magnetic poles 13a-13f can also have an influence on 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.
  • FIG. 5 shows, by way of example, characteristic curves 30 to 33 of a possible control of a linear motor 14 as shown in FIG. 1 or in FIG is operated by the reciprocating compressor 15.
  • the characteristic curve 30 shows the stroke X of the linear motor 14 as a function of the time t during a complete cycle from bottom dead center XUTP to top dead center XOTP and back.
  • the characteristic curve 31 shows the speed of the linear motor rotor 10 as a function of time t, the linear motor 14 being controlled in such a way that the speed of the linear motor rotor 10 as a function of time in
  • Section 31a increases linearly, is constant in section 31b, 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 is at a standstill, as can be seen from the characteristic curve 30, it has reached the top dead center XOTP.
  • the speed of the linear motor rotor 10 increases linearly in section 31e with a negative sign, remains constant in section 3 lf, and decreases linearly in section 13g until the linear motor rotor 10 comes to a standstill at bottom dead center XUTP.
  • 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 being decelerated with constant negative acceleration, and in the sections 32b, 32d and 32f is moved without acceleration.
  • the characteristic curve 33 shows the force exerted by the linear motor 14 on the linear motor rotor 10 as a function of time t, with a constant acceleration force being applied in section 33a, with a low constant force being applied in section 33b to overcome the force when moving
  • the linear motor rotor 10 is 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 XUTP until it comes to a standstill braked.
  • the linear motor 14 brakes the linear motor rotor 10, whereby the energy released can 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 one Energy store, is preferably temporarily stored in the control device.
  • the linear motor 14 can be controlled via a corresponding control through a variety of possibilities in function of the time t or the stroke X, with preferably at least one of the characteristics of stroke, Speed, acceleration and motor force is specified as a function of time t, the control device controlling the linear motor 14 in such a way that it moves at least approximately in accordance with the
  • FIG. 6 shows a further 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 35 shows the speed, the characteristic 36 the acceleration and the characteristic 37 the motor force of the linear motor 14 as a function of time t.
  • the course of the characteristic curve according to FIG. 6 shows a course similar to the course of the characteristic curve according to FIG. 5, the time axis in FIG. 6 being significantly shorter, i.e. the movement in FIG. 6 runs much faster, which can also be seen from the fact that the values for speed, acceleration and motor power in FIG. 6 are much higher than in FIG.
  • Control method has the advantage that all characteristics 34, 35, 36, and 37 change continuously between time t2 and time t3 and have no kinks, which means that the linear motor 14 is operated more gently, since kinks usually cause a sudden change in the operating behavior, which results in increased mechanical stress.
  • the control example shown in FIG. 6 is only one example of a large number of possibilities for controlling the linear motor 14.
  • the possibility of operating the linear motor 14 with a large number of different characteristic curves as a function of time has the advantage that a reciprocating piston 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 has at least one
  • State variable Z soii is specified as a function of time t or as a function of stroke X, the linear motor 14 being controlled in such a way that the free piston arrangement 16 has the specified state variable Z soii or at least approximately assumes it.
  • This Control method allows the operation of the linear motor compressor 1 to be optimized, for example, with regard to specifiable key figures by
  • the maximum force to be output by the linear motor 14, the maximum power required to operate the linear compressor 1, the maximum acceleration and / or the maximum speed is specified, 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 comprises an electric linear motor 14 and a reciprocating compressor 15 driven by this.
  • 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, the
  • the overall dynamics are essentially determined by the acting inertial forces, by the electromagnetic forces caused by the linear motor 14, by those caused by the reciprocating compressor 15 or in the
  • Reciprocating compressor 15 acting gas forces, as well as frictional forces caused by the movement of the piston and the linear motor 14.
  • Linear motor 14 produced a force in a reciprocating motion in the direction of stroke X.
  • the first piston 3 moves back and forth in a positive stroke direction X in the area between the bottom dead center XUTP and the top dead center XOTP.
  • the second piston 4 moves
  • F pr and F pi are the forces which act on the first and second pistons 3, 4 due to the gas pressure in the right, second and left, first compression chambers 5b, 5a, and F & and Fn are the frictional forces of the right, second piston 4 and the left, first piston 3, respectively.
  • the force caused by the gas pressure on the first or second piston 3, 4 can be calculated according to the following equation:
  • the control device can be given a state variable Z soii , the control device controlling the linear motor 14 in such a way that the linear motor compressor 1 at least approximately has the given state variable Z soii .
  • a stroke path point Xi i.e. a defined point along the stroke X
  • a setpoint speed v soii and / or a setpoint acceleration asoii and / or a setpoint force F soii of the free piston arrangement 16 can be specified as the state variable Z so u.
  • a travel time TLI could also be specified, that is to say a defined point in time within the
  • Total cycle time T the bottom dead center XUTP preferably being used as the reference for the time measurement.
  • the state variable Z soii can thus be im
  • a travel time point T LI and a setpoint speed v soii and / or a setpoint acceleration a soii and / or a setpoint force F so n of the free piston arrangement 16 associated therewith can also be specified. If, for example, as shown in FIG. 9, it is a matter of ensuring that the
  • Hubwegtician Xi specifies the speed v soii and at the Hubweg gleich X2 the speed -v Soii .
  • a setpoint acceleration a soii and / or a setpoint force F soii could of course also be specified at a point of travel path.
  • the state variable Z soii is a course of the state variable Z soii to be maintained during part of the total cycle time T and preferably during the total cycle time T
  • a speed- displacement curve between bottom dead center XUTP and top dead center XOTP and / or top dead center XOTP and bottom dead center XUTP is specified as the state variable Z soii , according to which the free piston arrangement 16 during operation of the in Figure 2 shown linear motor compressor 1 is moved back and forth.
  • FIG. 7 shows an example of such an operating method of the linear motor compressor 1, including both the linear motor 14 and the reciprocating compressor 15.
  • FIG. 7 shows the state variable Z soii
  • FIG. 7 shows on the left-hand side, to the left of point A, the movement of the first piston 3, which, starting from point A, the bottom dead center Xpru, moves according to the curve Gi via point B shown in FIG. 1 to point C. moves, the top dead center XOTP, and the according to the course G 2 via point D back to point A, the bottom dead center XFTU.
  • the diagram according to FIG. 7 shows on the right side, to the right of point A, the state variable Z so n
  • the curves G 2 and G 4 also have an identical curve, with the exception of the different sign of the speed.
  • the linear motor compressor 1 is preferably moved between the bottom dead center XUTP and the top dead center XOTP and on the way back between the top dead center XOTP and the bottom dead center XUTP with the same state variable Zsoii or with the same speed-path curve, so that all courses, with the exception of different signs relate to speed, have the same profile Gi, G 2 , G 3 , G 4 .
  • the first piston 3 has a first average speed V mi between points A and B, the compression phase AB, and the piston 3 has a second average speed between points B and C, the ejection phase BC V m2 on, the first being middle
  • Speed V mi is greater than the second mean speed V m2 .
  • the mean speed is understood to mean the mean speed value of the piston 3 or 4 between two points.
  • the first mean speed V mi thus corresponds to the mean speed between points A and B, or the first mean speed V mi corresponds to the time integral of the speed V (t) between points A and B, divided by the time it took to move of the piston 3 between points A and B is required, or corresponds the first mean speed V mi is the integral of the speed V (X) along the path X between points A and B divided by the
  • Speed V m 2 thus corresponds to the mean speed between points B and C, or the second mean speed
  • Speed V m 2 is the integral of the speed V (t) or V (X) between points B and C, divided by the time or distance BC, which is required to move piston 3 between points B and C.
  • Speed V m 3 is greater than the fourth mean speed V m 4.
  • the third mean speed V m 3 thus corresponds to the mean
  • Speed between points C and D, or the third mean speed Vm3 corresponds to the integral of the speed V (t) or V (X) between points C and D, divided by time
  • the fourth mean speed V m 4 thus corresponds to the averaged speed between points D and A, or the fourth mean speed V m 4 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 points D and A.
  • the linear motor compressor 1 is preferably operated in such a way that the pistons 3 and 4 are identical in their to-and-fro movement, apart from the reflections required on the axes according to FIG. 7
  • Speed-distance curves Gi and G4 or identical Have speed-distance curves G2 and G3.
  • the two pistons 3 and 4 each have a different speed-path curve when they move back and forth, for example a different, different speed-path curve when they move from right to left than when moving them from left to right.
  • Reciprocating compressor 15 understandable. Starting from point A to stroke point X3, curve Gi exhibits a relatively rapid rise, which is due in particular to the fact that small forces are still required in reciprocating compressor 15 at the beginning 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 driving force of the
  • top dead center XOTP which is preferably done in that the linear motor 14 generates a braking force and is advantageously operated as a generator, wherein the generated electrical energy is preferably temporarily stored in a control device, for example in order to accelerate the free piston arrangement 16 in section AX 3 again.
  • FIG. 7 shows a speed-path diagram (vx diagram) as the state variable Z so n.
  • vx diagram speed-path diagram
  • one of the characteristic curves 30 to 37 shown in FIGS. 5 or 6 could also be specified as the state variable Z soii , for example stroke, speed, acceleration or force as a function of time.
  • a combination of several of the characteristic curves 30 to 37 shown in FIGS. 5 or 6 could also be specified, for example by selecting the state variable Z such that, for example, a maximum speed and / or acceleration and / or the force to be output by the linear motor 14 and / or electrical energy consumed by the linear motor 14 is not exceeded.
  • the free piston arrangement 16 is moved from bottom dead center XUTP during a compression phase AB to the opening point B of the exhaust valve 6 with a predetermined speed-travel curve Gi such that the linear motor 14 can deliver a constant or essentially constant power Has.
  • the power is calculated from that to be generated by the linear motor 14
  • the linear motor 14 can be operated as a generator, at least along a section of the relaxation phase CD, by the linear motor 14 being driven by the relaxation forces Caused movement of the piston 3.4 brakes by a generator operation, the electrical energy generated thereby preferably
  • the linear motor 14 along at least a portion of the
  • This method ensures that the energy released by the gas located in the dead space Vtot during the expansion along the expansion phase CD is preferably completely converted into kinetic energy of the free piston arrangement 16, which is a
  • Figure 8 shows a further advantageous method of operating the linear motor compressor 1 shown in Figure 2.
  • Figure 8 shows a more schematic, i.e. A slightly idealized speed-travel 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 process in progress, and the diagram then pointing to the right the speed of the first Piston 3 in
  • Compression phase AB is going at a relatively high rate, in particular with a relatively high first average speed V mi , and thus traversed relatively quickly in time.
  • the speed v is reduced so that the
  • Compression phase AB lower second mean speed V m 2 is moved.
  • the free piston assembly 16 is starting from bottom dead center XUTP during a compression phase AB to the opening point B des
  • Linear motor compressor this is advantageously operated in such a way that the first average speed V mi during the compression phase AB high, preferably as high as possible, and that the second mean speed V m 2 is preset to be lower than the first mean speed V mi , preferably as low as possible, but in such a way that the preset cycle time Tz of a complete back and forth movement is maintained.
  • the duration of the discharge phase BC can be lengthened or the outflow speed of the gas from the
  • Cylinder interior can be reduced at the exhaust valve 6a, which is the
  • the linear motor 8 drives the
  • Free piston assembly 16 at least during a portion of the
  • Free piston assembly 16 at least during a portion of the
  • Decelerates exhaust phase BC and is preferably operated as a generator, which releases electrical energy, which is preferably
  • 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 mi during the compression phase AB is higher than the second average speed V m 2 during the exhaust phase BC.
  • the state variable Z soii according to the course G2 shows the movement of the
  • FIG. 9 shows a further operating method of the one shown in FIG.
  • Gradients Gi and G2 are selected such that the first and the second piston 3, 4 in the area of the points A, B, C and D move at a low or reduced speed v, the speed at the points C and A increasing 0 m / s is reduced because the free piston arrangement is attached to this
  • Reversal points comes to a standstill for a short time.
  • the speed is in the region of points C and A, i. in particular
  • Figures 9a and 9b show the speed of Figure 9 in the area of point C and A in detail.
  • the speed at points C and A is very low, and is, for example, less than 0.1 m / s.
  • the reduced speed in points C and A has the consequence that the inlet valve 7a and the outlet valve 6a are closed at low speed, which means that these valves are only slightly mechanically 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 bottom dead center XUTP, first with a greater negative acceleration, and then braked with a reduced negative acceleration, the
  • a state variable Z so u can only consist of a single point, for example, as shown in FIG. 9, the stroke path point Xi with the value v so n.
  • the control is therefore such that the free piston arrangement 16 has the speed v soii at the stroke path point Xi . This ensures that the
  • Speed of the free piston arrangement 16 at the stroke path point Xi has the desired, low speed v soii .
  • FIG. 10 shows a control device 20 for operating a
  • Linear motor compressor 1 A control device 27 detects an actual state variable 29a with at least one sensor 21 via a signal line, at least one actual state variable of the linear motor compressor 1,
  • the setpoint is a
  • the control device 27 calculates from the actual state variable 29a and the target state variable Z soii 29e
  • Control signal 29b 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 use electrical conductors 24a, 24b, 24c, 24d to generate a plurality of stator windings 12a, 12b, 12c, 12d to be controlled individually.
  • the power supply 23 is via a
  • Power line 25 is connected to the inverter 22.
  • the energy supply 23 comprises a
  • the inverter 22 being controllable in such a way that electrical energy can be withdrawn from the linear motor compressor 1 and can be 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 a 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)

Abstract

L'invention concerne un procédé pour faire fonctionner un compresseur à moteur linéaire (1) comprenant un moteur linéaire (14) électrique, un cylindre (2) et un ensemble à piston libre (16) à mouvement linéaire comprenant un piston (3), le cylindre (2) et le piston (3) formant une chambre de compression (5), l'ensemble à piston libre (16) étant entraîné directement par le moteur linéaire (14) et déplacé selon un mouvement de va-et-vient le long de sa course (X) entre un point mort haut (XOTP) et un point mort bas (XUTP), un fluide étant introduit dans la chambre de compression (5) par l'extérieur, ce fluide introduit étant comprimé ou décomprimé dans la chambre de compression (5) puis à nouveau évacué vers l'extérieur, au moins un paramètre d'état (Zsoll) étant prédéfini pour le compresseur à moteur linéaire (1), le moteur linéaire (14) étant commandé de manière que le compresseur à moteur linéaire (1) présente ce paramètre d'état (Zsoll) prédéfini.
EP20705144.2A 2019-02-05 2020-02-05 Procédé de fonctionnement d'un compresseur de moteur linéaire et compresseur de moteur linéaire Active EP3921541B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP19155631 2019-02-05
PCT/EP2020/052913 WO2020161210A1 (fr) 2019-02-05 2020-02-05 Procédé pour faire fonctionner un compresseur à moteur linéaire, et compresseur à moteur linéaire

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EP3921541A1 true EP3921541A1 (fr) 2021-12-15
EP3921541B1 EP3921541B1 (fr) 2022-10-19

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EP (1) EP3921541B1 (fr)
JP (1) JP7528101B2 (fr)
KR (1) KR20210125013A (fr)
CN (1) CN113795671B (fr)
WO (1) WO2020161210A1 (fr)

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Publication number Priority date Publication date Assignee Title
JPS59221401A (ja) * 1983-06-01 1984-12-13 Hitachi Ltd フリ−ピストン機関のガススプリング制御装置
FR2662215B1 (fr) * 1990-05-15 1994-10-21 Oreal Dispositif de compression, en particulier pour le remplissage sous pression d'un reservoir.
JPH0868379A (ja) * 1994-08-29 1996-03-12 Oriental Motor Co Ltd リニアパルスモータを備えた往復形ポンプ
JP3118413B2 (ja) * 1996-04-30 2000-12-18 三洋電機株式会社 リニアコンプレッサの駆動装置
JP2003148339A (ja) 2001-11-15 2003-05-21 Matsushita Electric Ind Co Ltd リニア圧縮機
NZ515578A (en) * 2001-11-20 2004-03-26 Fisher & Paykel Appliances Ltd Reduction of power to free piston linear motor to reduce piston overshoot
JP2004003408A (ja) 2002-04-25 2004-01-08 Kazumasa Ikuta 流体の吸引吐出装置
US7456592B2 (en) * 2003-12-17 2008-11-25 Lg Electronics Inc. Apparatus and method for controlling operation of reciprocating compressor
JP4696491B2 (ja) 2004-08-05 2011-06-08 ダイキン工業株式会社 圧縮機の制御装置及び制御方法並びに空調機及びその制御方法
DE102007034293A1 (de) * 2007-07-24 2009-01-29 BSH Bosch und Siemens Hausgeräte GmbH Hubgeregelter Linearverdichter
CN102472265B (zh) * 2009-07-23 2015-07-01 伯克哈特压缩机股份公司 供给量控制方法和具有供给量控制功能的往复活塞式压缩机
JP2011127879A (ja) 2009-12-21 2011-06-30 Aisin Seiki Co Ltd 往復動型膨張圧縮機
AU2011211430B2 (en) 2010-02-23 2013-08-29 Artemis Intelligent Power Limited Fluid-working machine valve timing
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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CN113795671B (zh) 2023-09-01
EP3921541B1 (fr) 2022-10-19
JP7528101B2 (ja) 2024-08-05
KR20210125013A (ko) 2021-10-15
WO2020161210A1 (fr) 2020-08-13
JP2022518852A (ja) 2022-03-16
CN113795671A (zh) 2021-12-14

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