EP3714162B1 - Method for operating a piston compressor and piston compressor - Google Patents

Method for operating a piston compressor and piston compressor Download PDF

Info

Publication number
EP3714162B1
EP3714162B1 EP18803317.9A EP18803317A EP3714162B1 EP 3714162 B1 EP3714162 B1 EP 3714162B1 EP 18803317 A EP18803317 A EP 18803317A EP 3714162 B1 EP3714162 B1 EP 3714162B1
Authority
EP
European Patent Office
Prior art keywords
piston
hydraulic
volume
medium
reciprocating
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
EP18803317.9A
Other languages
German (de)
French (fr)
Other versions
EP3714162A1 (en
Inventor
Sascha Dorner
Christoph Nagl
Johannes FRITZER
Klaus Fischer
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.)
Linde GmbH
Original Assignee
Linde GmbH
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 Linde GmbH filed Critical Linde GmbH
Publication of EP3714162A1 publication Critical patent/EP3714162A1/en
Application granted granted Critical
Publication of EP3714162B1 publication Critical patent/EP3714162B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • 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
    • F04B25/00—Multi-stage pumps
    • F04B25/005—Multi-stage pumps with two cylinders
    • 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
    • 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
    • F04B39/0027—Pulsation and noise damping means
    • 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
    • F04B39/10—Adaptations or arrangements of distribution members
    • 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
    • F04B49/16—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 by adjusting the capacity of dead spaces of working chambers
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/02—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having two cylinders
    • 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
    • F04B19/20—Other positive-displacement pumps
    • F04B19/22—Other positive-displacement pumps of reciprocating-piston type
    • 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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/005—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders with two cylinders
    • 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
    • F04B49/002—Hydraulic systems to change the pump delivery
    • 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
    • F04B49/08—Regulating by delivery pressure
    • 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
    • F04B49/22—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 by means of valves
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • 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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/103—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber
    • F04B9/107—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber rectilinear movement of the pumping member in the working direction being obtained by a single-acting liquid motor, e.g. actuated in the other direction by gravity or a spring
    • 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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/109—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers

Definitions

  • the invention relates to a method for operating a reciprocating compressor and a reciprocating compressor.
  • any of the pamphlets DE 10 2007 033 601 B3 and AT 3213 U1 discloses a method for operating a reciprocating compressor and a reciprocating compressor with a reciprocating piston in a cylinder, an inlet valve and an outlet valve being provided in the cylinder on the side of a medium to be compressed and conveyed, with a hydraulic drive with a hydraulic piston using the reciprocating piston a hydraulic medium is moved back and forth in a first volume with which the reciprocating piston is acted upon on the side of the hydraulic drive.
  • Compressors are used in particular to compress gaseous media.
  • the efficiency of conventional reciprocating compressors is strongly influenced by the presence of residual volume or dead space in the top dead center. Gas or medium in this area leads to a re-expansion and a reduction in the possible inflowing flow rate in the suction cycle.
  • This area is unavoidable in order to compensate for manufacturing tolerances and thermal expansion of the components and subsequently to avoid mechanical contact of the reciprocating piston with the cylinder head in the compressor.
  • Channels for the suction and discharge valves i.e. inlet and outlet valves
  • ionic compressors in particular piston compressors, are operated hydraulically on the one hand and compress a two-phase mixture consisting of a medium or gas and a liquid lubricant (i.e. an ionic liquid), which does not evaporate and for this reason are completely separated again by a simple separation process can.
  • a liquid lubricant i.e. an ionic liquid
  • the advantage of such an ionic compressor is that by using a liquid phase in the compression chamber, the dead space in the cylinder can be reduced to a minimum, thereby optimizing the efficiency of the compression process.
  • the disadvantage is the additional component loads and the resulting increased noise emissions due to the characteristics similar to a liquid hammer.
  • an oil fill quantity must be checked and compensated if necessary.
  • the main problems arise from mechanical contacts in the reversal points of the reciprocating pistons and, as a result, increased component stress as well Noise emissions, which are particularly problematic when installed in the vicinity of residential areas and which require additional sound insulation.
  • the task arises of providing a way of improving the operation of a reciprocating compressor, in particular with regard to component loading and noise emissions.
  • the invention is based on a method for operating a piston compressor with a reciprocating piston in a cylinder, with an inlet valve and an outlet valve (or a suction valve and a pressure valve) in the cylinder on the side of a medium to be compressed and conveyed (i.e. in the cylinder head) are provided.
  • a hydraulic drive comprising a hydraulic piston
  • the reciprocating piston is moved back and forth (or up and down) using a hydraulic medium in a first volume with which the reciprocating piston is acted on on the hydraulic drive side.
  • the reciprocating piston oscillates in the cylinder between two reversal points, the so-called bottom dead center (BDC) and the so-called top dead center (TDC).
  • BDC bottom dead center
  • TDC top dead center
  • the reciprocating piston would be moved synchronously with the hydraulic piston.
  • the reciprocating piston due to leakage effects in the circuit of the hydraulic medium (i.e. the aforementioned first volume) it can happen that the reciprocating piston is no longer moved synchronously with the hydraulic piston. This means that, for example, at bottom dead center, the reciprocating piston hits the cylinder base, but the hydraulic piston moves even further downwards. This creates a negative pressure in the first volume or in the hydraulic circuit.
  • the reciprocating piston can also hit the cylinder head while the hydraulic piston moves further upwards. This creates an overpressure in the first volume or in the hydraulic circuit.
  • hydraulic medium is fed into the first volume and / or is discharged from the first volume.
  • the position of the hydraulic piston and the angle of rotation of the shaft provided for moving the hydraulic piston are linked to one another and indicate a current position of the hydraulic drive.
  • the position of the reciprocating piston and the pressure in the first volume are also linked to one another, to the extent that the pressure rises or falls when the reciprocating piston hits the cylinder. If these variables are now determined, they can be set in relation to one another, so that it can be recognized whether a stop of the reciprocating piston occurs or, if applicable, whether such a stop of the reciprocating piston is imminent. Accordingly, hydraulic medium can then be fed into the first volume or removed from the first volume.
  • the negative pressure arising in the first volume or in the hydraulic circuit can be counteracted by supplying hydraulic medium.
  • the attack can In this way, the impact can be reduced or even prevented, which causes a reduction in noise emissions and the load on the component.
  • a stop at the top dead center can be reduced or even prevented by the removal of hydraulic medium, which also has the effect of reducing the noise emissions and the component load.
  • suitable valves can be provided which are actuated accordingly, i.e. opened or closed.
  • a hydraulic damping unit using the hydraulic medium and forming a second volume which is at least partially delimited by the reciprocating piston, limits a movement of the reciprocating piston on the hydraulic drive side if necessary.
  • a damping unit can be used not only to further dampen the movement of the reciprocating piston, but also to set a compression ratio.
  • the second volume is preferably connected to the first volume in order to reduce an amount of medium to be conveyed by means of the piston compressor. This goes hand in hand with an increase in dead space in the cylinder head.
  • Excess hydraulic medium (that is to say in order to reduce hydraulic medium in the second volume) is for this purpose discharged from the first volume into a reservoir.
  • the first volume is connected to the reservoir for the hydraulic medium in order to increase an amount of medium to be conveyed by means of the piston compressor. This goes hand in hand with a reduction in dead space in the cylinder head.
  • the required hydraulic medium (that is to say to increase the amount of hydraulic medium in the second volume or to fill the second volume) is supplied from the reservoir.
  • the second volume can therefore be filled with a more or less hydraulic medium. Since the movement of the reciprocating piston in the direction of bottom dead center (i.e. in the direction of the hydraulic drive) can be limited by the hydraulic medium in the second volume, the volume which is at the Cylinder head or at top dead center is available for compression, can be changed. Accordingly, the compression ratio can be changed.
  • a multistage piston compressor with at least two reciprocating pistons and corresponding cylinders is advantageously used as the piston compressor.
  • a movement of these reciprocating pistons in the corresponding cylinders can, however, still take place with the one hydraulic drive, then with a corresponding number of such first volumes. It goes without saying that a number of such damping units can then also be provided accordingly.
  • the individual cylinders can then be arranged in a row or in a star shape, for example. The compression then takes place in such a way that medium ejected from one cylinder is fed to another cylinder and is further compressed there.
  • an ionic liquid is used as working fluid [is.
  • an ionic compressor is also used.
  • ionic compressors offer advantages such as a reduced dead volume.
  • the supply and discharge of hydraulic medium proposed here can now also reduce the remaining disadvantages of noise emission and component wear.
  • the invention also relates to a piston compressor with a reciprocating piston in a cylinder, an inlet valve and an outlet valve being provided in the cylinder on the side of a medium to be compressed and conveyed.
  • the piston compressor has a hydraulic drive with a hydraulic piston, by means of which the reciprocating piston can be moved back and forth using a hydraulic medium in a first volume with which the reciprocating piston can be acted upon on the hydraulic drive side.
  • At least one measuring device is provided, by means of which a position of the hydraulic piston and / or an angle of rotation of a shaft provided for moving the hydraulic piston and a position of the reciprocating piston and / or a pressure in the first volume can be determined.
  • the piston compressor is now set up to supply hydraulic medium into the first volume as required depending on the position of the hydraulic piston and / or the angle of rotation of the shaft provided for moving the hydraulic piston in relation to the position of the reciprocating piston and / or the pressure in the first volume and / or to be discharged from the first volume.
  • the reciprocating compressor preferably also has a hydraulic damping unit by means of which a movement of the reciprocating piston on the hydraulic drive side can be limited if necessary using the hydraulic medium and forming a second volume which is at least partially limited by the reciprocating piston.
  • a first valve, by means of which the second volume can be connected to the first volume, and a second valve, by means of which hydraulic medium can be discharged from the first volume into a reservoir for the hydraulic medium, are advantageously provided. In this way, an amount of medium to be conveyed by means of the piston compressor can be reduced. It is also preferred if a third valve is provided, by means of which the first volume can be connected to the reservoir for the hydraulic medium. Hydraulic medium can thus be fed to the first volume.
  • This third valve can preferably also be designed in such a way that hydraulic medium can be automatically fed from the reservoir to the first volume when the pressure on the first volume side is lower than that on the reservoir side.
  • the third valve can be designed, for example, as a check valve.
  • the piston compressor is advantageously designed as a multi-stage piston compressor with at least two reciprocating pistons and corresponding cylinders.
  • An ionic liquid is expediently provided as the operating liquid in the reciprocating compressor.
  • FIG. 1 a piston compressor 100 according to the invention is shown schematically in a preferred embodiment, which is suitable for carrying out a method according to the invention.
  • the piston compressor 100 also referred to as a reciprocating compressor in the form shown, here comprises a cylinder 110 in which a reciprocating piston 111 can be moved back and forth or up and down.
  • a reciprocating compressor can be designed in several stages, i.e. several of the cylinders 110 shown with reciprocating pistons 111 can be present.
  • the following description in relation to the cylinder with reciprocating piston then also applies accordingly to other cylinders with reciprocating pistons.
  • the piston compressor 100 is driven by a hydraulic drive or a hydraulic drive, which here comprises a hydraulic piston 120.
  • the hydraulic piston 120 is driven by a planet wheel with a shaft 121 with a suitable linkage (hydraulic crank drive).
  • hydraulic medium a hydraulic oil
  • the reciprocating piston 111 oscillates in the cylinder 110 between two reversal points, which are referred to as bottom dead center (BDC) and top dead center (TDC).
  • the frequency at which the shaft rotates and the reciprocating piston moves up and down can be between 0.5 Hz and 12 Hz (but is usually kept constant), the stroke of the reciprocating piston can for example be between 30mm and 100mm lie.
  • the stroke or the stroke volume of the hydraulic piston is usually also constant.
  • the hydraulic medium a is thus conveyed to the bottom side of the reciprocating piston 111 here.
  • the reciprocating piston 111 is accordingly moved upwards and compresses a two-phase mixture in the so-called gas cylinder 114, that is to say the upper region of the cylinder.
  • This two-phase mixture here comprises, on the one hand, a medium b to be compressed and conveyed and, on the other hand, an ionic operating fluid. If the pressure in the cylinder 110 exceeds the counter pressure at the pressure valve or outlet valve 113, this is opened and the medium b is conveyed approximately isobarically into the pressure range until the top dead center is reached.
  • the required amount can now be calculated and corrected within the scope of the present invention, for example via a data comparison between a measuring device 161 (for example a displacement measuring system) and a measuring device 160 (for example a rotation angle sensor). While the position x of the reciprocating piston 111 can be determined by means of the measuring device 161, for example, a rotational angle ⁇ of the shaft 121 can be determined with the measuring device 160. In addition, a pressure p in the first volume 141 can also be recorded, for example, by means of a suitable measuring device 162.
  • a measuring device 161 for example a displacement measuring system
  • a measuring device 160 for example a rotation angle sensor
  • a strike of the reciprocating piston 111 on the cylinder head is now recognized by an increase in pressure at the end of the actually isobaric expulsion phase, as a result of which the excess hydraulic medium is conveyed back into the reservoir 130 via a pressure limiter valve 154.
  • a damping unit 140 is provided, by means of which an adaptive damping system can be implemented, regardless of the frequency, of the pressure conditions in the piston compressor and of the leakage in the hydraulic area.
  • This damping unit 140 can be used to dampen the downward movement of the reciprocating piston 111 and thus to reduce the noise emissions and mechanical loads during the movement in the direction of bottom dead center.
  • a first valve 150 is closed.
  • the reciprocating piston 111 is prevented from moving in the direction of bottom dead center or in the direction of the hydraulic drive, although the hydraulic piston 120 is moving downward.
  • the required amount of hydraulic medium is sucked into the circuit or into the first volume 141 via the non-return valve 153 as a result of the negative pressure that occurs. If the hydraulic piston 120 moves upwards again, the system is closed and the reciprocating piston 111 has been raised by a defined volume (due to the additional amount of hydraulic medium carried), whereby the dead space is reduced and the conveyed amount of medium to be compressed is increased.
  • the third valve 155 can be opened and the filling amount reduced.
  • the first valve 150 is opened so as not to influence the downward movement of the reciprocating piston 111.
  • the second valve 155 is opened in order to reduce or discharge a defined amount of hydraulic medium, which takes place through the movement of the hydraulic piston 120 upwards. Once the required position of the reciprocating piston has been reached, the first valve 150 can be closed again.
  • the hydraulic piston 120 If this is done by the hydraulic piston 120 before the bottom dead center is reached, the latter delivers the necessary amount of hydraulic medium via the check valve 153.
  • a change in the pressure in the system is directly proportional to the position of the reciprocating piston 111.
  • a deviation in the position x of the reciprocating piston 111 assigned to the angle of rotation ⁇ of the shaft 121 due to leakage can be caused by the blocking of the reciprocating piston 111 by means of the damping unit 140, hydraulic medium is replenished via the check valve 153 and the misalignment is compensated.
  • This adaptive damping system makes it possible to optimize hydraulically driven piston compressors with regard to the usable stroke volume. It is possible to make the piston travel variable and, depending on the requirements of the system, to optimize it in terms of delivery rate, pressure and effectiveness.
  • the remaining volume between the reciprocating piston and the cylinder head expands when the reciprocating piston moves downwards and, depending on its size, influences the opening time of the normally spring-operated suction valve.
  • An extension of an existing or already delivered piston compressor to a proposed piston compressor allows the optimization of the operating parameters and an increase in efficiency. It is also possible to increase existing service life and reduce vibrations and noise emissions.
  • an existing system i.e. an existing reciprocating compressor or several of them
  • a position measuring system and a rotary encoder in the sense of the mentioned measuring devices
  • the automation programming of the system can be expanded to include the necessary control routines.
  • Another embodiment consists in the fact that it is possible to implement an expander system in connection with controllable suction and pressure valves, for example on a piezoelectric basis, as they are used, for example, in automotive applications.
  • Such a system uses the expansion work during the expansion of the gas, for example in a dispenser system, in which gas at a lower pressure level is required, and can thus be used to generate electricity on the basis of an energy recovery system.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Reciprocating Pumps (AREA)

Description

Die Erfindung betrifft ein Verfahren zum Betreiben eines Kolbenverdichters sowie einen Kolbenvrdichter.The invention relates to a method for operating a reciprocating compressor and a reciprocating compressor.

Jede der Druckschriften DE 10 2007 033 601 B3 und AT 3213 U1 offenbart ein Verfahren zum Betreiben eines Kolbenverdichters und einen Kolbenverdichter mit einem Hubkolben in einem Zylinder, wobei in dem Zylinder auf Seiten eines zu verdichtenden und zu fördernden Mediums ein Einlassventil und ein Auslassventil vorgesehen sind, wobei mit einem hydraulischen Antrieb mit einem Hydraulikkolben der Hubkolben unter Verwendung eines hydraulischen Mediums in einem ersten Volumen, mit dem der Hubkolben auf Seiten des hydraulischen Antriebs beaufschlagt wird, hin und her bewegt wird.Any of the pamphlets DE 10 2007 033 601 B3 and AT 3213 U1 discloses a method for operating a reciprocating compressor and a reciprocating compressor with a reciprocating piston in a cylinder, an inlet valve and an outlet valve being provided in the cylinder on the side of a medium to be compressed and conveyed, with a hydraulic drive with a hydraulic piston using the reciprocating piston a hydraulic medium is moved back and forth in a first volume with which the reciprocating piston is acted upon on the side of the hydraulic drive.

Verdichter werden insbesondere zum Verdichten von gasförmigen Medien eingesetzt. Die Effizienz von herkömmlichen Kolbenverdichtern wird sehr stark durch das Vorhandensein von Restvolumen bzw. Totraum im oberen Totpunkt beeinflusst. Gas bzw. Medium in diesem Bereich führt zu einer Rückexpansion und einer Verringerung der im Saugtakt möglichen einströmenden Fördermenge. Dieser Bereich ist unvermeidbar, um Fertigungstoleranzen und Wärmedehnungen der Bauteile zu kompensieren und in weiterer Folge mechanischen Kontakt der Hubkolben mit dem Zylinderkopf im Verdichter zu vermeiden. Kanäle für die Saug- und Druckventile (d.h. Einlass- und Auslassventile) erhöhen diesen negativen Effekt.Compressors are used in particular to compress gaseous media. The efficiency of conventional reciprocating compressors is strongly influenced by the presence of residual volume or dead space in the top dead center. Gas or medium in this area leads to a re-expansion and a reduction in the possible inflowing flow rate in the suction cycle. This area is unavoidable in order to compensate for manufacturing tolerances and thermal expansion of the components and subsequently to avoid mechanical contact of the reciprocating piston with the cylinder head in the compressor. Channels for the suction and discharge valves (i.e. inlet and outlet valves) increase this negative effect.

Die Reduzierung dieses Totraums verringert die Rückexpansion des verbleibenden Mediums und erhöht dadurch die Fördermenge bzw. den Wirkungsgrad des Verdichtungsprozesses. Sog. ionische Verdichter, insbesondere Kolbenverdichter, werden einerseits hydraulisch betrieben und verdichten andererseits ein Zweiphasengemisch bestehend aus einem Medium bzw. Gas und einem flüssigen Schmiermittel (also eine ionische Flüssigkeit), welches nicht verdampft und aus diesem Grund durch einen einfachen Abscheideprozess wieder vollständig getrennt werden kann. Der Vorteil eines solchen ionischen Verdichters liegt darin, dass durch die Verwendung einer flüssigen Phase im Verdichtungsraum der Totraum im Zylinder auf ein Minimum reduziert werden kann und dadurch die Effizienz des Verdichtungsprozesses optimiert wird.The reduction of this dead space reduces the re-expansion of the remaining medium and thereby increases the delivery rate and the efficiency of the compression process. So-called ionic compressors, in particular piston compressors, are operated hydraulically on the one hand and compress a two-phase mixture consisting of a medium or gas and a liquid lubricant (i.e. an ionic liquid), which does not evaporate and for this reason are completely separated again by a simple separation process can. The advantage of such an ionic compressor is that by using a liquid phase in the compression chamber, the dead space in the cylinder can be reduced to a minimum, thereby optimizing the efficiency of the compression process.

Nachteilig ergeben sich die zusätzlichen Bauteilbelastungen und dadurch erhöhte Schallemissionen bedingt durch der einem Flüssigkeitsschlag ähnlichen Charakteristik. Zusätzlich müssen bei hydraulisch angetriebenen Verdichtungskonzepten aufgrund innerer Leckage im Hydraulikkreislauf eine Ölfüllmenge kontrolliert und bei Bedarf kompensiert werden. Hauptprobleme ergeben sich durch mechanische Kontakte in den Umkehrpunkten der Hubkolben und dadurch erhöhte Bauteilbelastung sowie Geräuschemissionen, welche vor allem bei einer Installation in der Nähe von Wohngebieten als problematisch zu betrachten sind und einer zusätzlichen Schallisolierung bedürfen.The disadvantage is the additional component loads and the resulting increased noise emissions due to the characteristics similar to a liquid hammer. In addition, with hydraulically driven compression concepts, due to internal leakage in the hydraulic circuit, an oil fill quantity must be checked and compensated if necessary. The main problems arise from mechanical contacts in the reversal points of the reciprocating pistons and, as a result, increased component stress as well Noise emissions, which are particularly problematic when installed in the vicinity of residential areas and which require additional sound insulation.

Aus dem Bereich des Automobilbaus ist beispielsweise das Konzept der Dämpfung, dort insbesondere bei Stoßdämpfern bekannt. Dabei wird kinetische Energie in Form von Schwingungen dissipiert. Dies ermöglicht neben der Reduktion unerwünschten Schwankens oder Schwingens des Fahrzeugs auch die Reduktion von Bauteilbelastungen und Schallemissionen.For example, the concept of damping is known from the field of automobile construction, there in particular in the case of shock absorbers. Kinetic energy is dissipated in the form of vibrations. In addition to reducing unwanted swaying or oscillation of the vehicle, this also enables component loads and noise emissions to be reduced.

Vor diesem Hintergrund stellt sich die Aufgabe, eine Möglichkeit bereitzustellen, den Betrieb eines Kolbenverdichters zu verbessern, insbesondere hinsichtlich Bauteilbelastung und Schallemission.Against this background, the task arises of providing a way of improving the operation of a reciprocating compressor, in particular with regard to component loading and noise emissions.

Offenbarung der ErfindungDisclosure of the invention

Diese Aufgabe wird durch ein Verfahren zum Betreiben eines Kolbenverdichters sowie einen Kolbenverdichter mit den Merkmalen der unabhängigen Patentansprüche gelöst. Bevorzugte Ausgestaltungen sind Gegenstand der abhängigen Patentansprüche sowie der nachfolgenden Beschreibung.This object is achieved by a method for operating a reciprocating compressor and a reciprocating compressor with the features of the independent claims. Preferred configurations are the subject of the dependent claims and the following description.

Vorteile der ErfindungAdvantages of the invention

Die Erfindung geht aus von einem Verfahren zum Betreiben eines Kolbenverdichters mit einem Hubkolben in einem Zylinder, wobei in dem Zylinder auf Seiten eines zu verdichtenden und zu fördernden Mediums (also im Zylinderkopf) ein Einlassventil und ein Auslassventil (bzw. ein Saugventil und ein Druckventil) vorgesehen sind. Mit einem hydraulischen Antrieb, der einen Hydraulikkolben umfasst, wird der Hubkolben unter Verwendung eines hydraulischen Mediums in einem ersten Volumen, mit dem der Hubkolben auf Seiten des hydraulischen Antriebs beaufschlagt wird, hin und her (bzw. auf und ab) bewegt.The invention is based on a method for operating a piston compressor with a reciprocating piston in a cylinder, with an inlet valve and an outlet valve (or a suction valve and a pressure valve) in the cylinder on the side of a medium to be compressed and conveyed (i.e. in the cylinder head) are provided. With a hydraulic drive comprising a hydraulic piston, the reciprocating piston is moved back and forth (or up and down) using a hydraulic medium in a first volume with which the reciprocating piston is acted on on the hydraulic drive side.

Der Hubkolben oszilliert dabei im Zylinder zwischen zwei Umkehrpunkten, dem sog. unteren Totpunkt (UT) und dem sog. oberen Totpunkt (OT). Bei der Bewegung in Richtung des oberen Totpunkts wird im Zylinder bzw. Zylinderkopf vorhandenes Medium verdichtet und dann durch das Auslassventil ausgestoßen, bei Bewegung in Richtung des unteren Totpunkts wird Medium durch das Einlassventil eingesaugt.The reciprocating piston oscillates in the cylinder between two reversal points, the so-called bottom dead center (BDC) and the so-called top dead center (TDC). When moving towards the top dead center, something is present in the cylinder or cylinder head Medium is compressed and then ejected through the outlet valve, when moving towards the bottom dead center, medium is sucked in through the inlet valve.

An sich würde hier der Hubkolben synchron mit dem Hydraulikkolben bewegt werden. Allerdings kann es aufgrund von Leckageeffekten im Kreislauf des hydraulischen Mediums (also des erwähnten ersten Volumens) vorkommen, dass der Hubkolben nicht mehr synchron mit dem Hydraulikkolben bewegt wird. Dies bedeutet, dass beispielsweise am unteren Totpunkt der Hubkolben am Zylinderboden anschlägt, sich der Hydraulikkolben aber noch weiter nach unten bewegt. Dadurch entsteht im ersten Volumen bzw. im Hydraulikkreislauf ein Unterdruck. Ebenso kann der Hubkolben am Zylinderkopf anschlagen, während sich der Hydraulikkolben noch weiter nach oben bewegt. Dadurch entsteht im ersten Volumen bzw. im Hydraulikkreislauf ein Überdruck.As such, the reciprocating piston would be moved synchronously with the hydraulic piston. However, due to leakage effects in the circuit of the hydraulic medium (i.e. the aforementioned first volume) it can happen that the reciprocating piston is no longer moved synchronously with the hydraulic piston. This means that, for example, at bottom dead center, the reciprocating piston hits the cylinder base, but the hydraulic piston moves even further downwards. This creates a negative pressure in the first volume or in the hydraulic circuit. The reciprocating piston can also hit the cylinder head while the hydraulic piston moves further upwards. This creates an overpressure in the first volume or in the hydraulic circuit.

Es ist nun vorgesehen, dass bei Bedarf in Abhängigkeit von einer Position des Hydraulikkolbens und/oder eines Drehwinkels einer zur Bewegung des Hydraulikkolbens vorgesehenen Welle in Relation zu einer Position des Hubkolbens und/oder einem Druck im ersten Volumen hydraulisches Medium in das erste Volumen zugeführt und/oder aus dem ersten Volumen abgeführt wird. Die entsprechenden Größen können dabei mittels einer oder mehrere geeigneter Messeinrichtungen ermittelt werden.It is now provided that, if necessary, depending on a position of the hydraulic piston and / or an angle of rotation of a shaft provided for moving the hydraulic piston in relation to a position of the reciprocating piston and / or a pressure in the first volume, hydraulic medium is fed into the first volume and / or is discharged from the first volume. The corresponding variables can be determined by means of one or more suitable measuring devices.

Die Position des Hydraulikkolbens und der Drehwinkel der zur Bewegung des Hydraulikkolbens vorgesehenen Welle sind miteinander verknüpft und geben eine aktuelle Position des hydraulischen Antriebs an. Die Position des Hubkolbens und der Druck im ersten Volumen sind ebenfalls miteinander verknüpft, und zwar insofern, als bei einem Anschlag des Hubkolbens im Zylinder der Druck ansteigt bzw. abfällt. Wenn nun diese Größen ermittelt werden, können sie in Relation zueinander gesetzt werden, sodass erkannt werden kann, ob ein Anschlag des Hubkolbens auftritt oder ggf. auch ob ein solcher Anschlag des Hubkolbens bevorsteht. Entsprechend kann dann hydraulisches Medium in das erste Volumen zugeführt bzw. aus dem ersten Volumen abgeführt werden.The position of the hydraulic piston and the angle of rotation of the shaft provided for moving the hydraulic piston are linked to one another and indicate a current position of the hydraulic drive. The position of the reciprocating piston and the pressure in the first volume are also linked to one another, to the extent that the pressure rises or falls when the reciprocating piston hits the cylinder. If these variables are now determined, they can be set in relation to one another, so that it can be recognized whether a stop of the reciprocating piston occurs or, if applicable, whether such a stop of the reciprocating piston is imminent. Accordingly, hydraulic medium can then be fed into the first volume or removed from the first volume.

Wenn oder bevor der Hubkolben am unteren Totpunkt am Zylinderboden anschlägt, kann so dem im ersten Volumen bzw. im Hydraulikkreislauf entstehenden Unterdruck durch Zufuhr von hydraulischem Medium entgegengewirkt werden. Der Anschlag kann Anschlag kann so gemindert oder gar verhindert werden, was eine Reduzierung der Schallemissionen und der Bauteilbelastung bewirkt.When or before the reciprocating piston strikes the bottom of the cylinder at bottom dead center, the negative pressure arising in the first volume or in the hydraulic circuit can be counteracted by supplying hydraulic medium. The attack can In this way, the impact can be reduced or even prevented, which causes a reduction in noise emissions and the load on the component.

Entsprechend kann durch die Abfuhr von hydraulischem Medium ein Anschlag am oberen Totpunkt gemindert oder gar verhindert werden, was ebenfalls eine Reduzierung der Schallemissionen und der Bauteilbelastung bewirkt. Hierzu können geeignete Ventile vorgesehen sein, die entsprechend betätigt, d.h. geöffnet oder geschlossen werden. Für eine detailliertere Beschreibung solcher Ventile sei an dieser Stelle auf die Beschreibung des Kolbenverdichters bzw. die Figurenbeschreibung verwiesen.Correspondingly, a stop at the top dead center can be reduced or even prevented by the removal of hydraulic medium, which also has the effect of reducing the noise emissions and the component load. For this purpose, suitable valves can be provided which are actuated accordingly, i.e. opened or closed. For a more detailed description of such valves, reference is made at this point to the description of the piston compressor or the description of the figures.

Vorzugsweise wird mit einer hydraulischen Dämpfungseinheit unter Verwendung des hydraulischen Mediums und unter Bildung eines zweiten Volumens, das zumindest teilweise von dem Hubkolben begrenzt wird, eine Bewegung des Hubkolbens auf Seiten des hydraulischen Antriebs bei Bedarf begrenzt. Eine solche Dämpfungseinheit kann nicht nur zum weiteren Dämpfen der Bewegung des Hubkolbens verwendet werden, sondern auch, um ein Verdichtungsverhältnis einzustellen.Preferably, a hydraulic damping unit using the hydraulic medium and forming a second volume which is at least partially delimited by the reciprocating piston, limits a movement of the reciprocating piston on the hydraulic drive side if necessary. Such a damping unit can be used not only to further dampen the movement of the reciprocating piston, but also to set a compression ratio.

Hierzu wird bevorzugt das zweite Volumen mit dem ersten Volumen verbunden, um eine mittels des Kolbenverdichters zu fördernde Menge an Medium zu reduzieren. Dies geht einher mit einer Erhöhung von Totraum im Zylinderkopf. Überschüssiges hydraulisches Medium (also um im zweiten Volumen hydraulisches Medium abzubauen) wird hierzu aus dem ersten Volumen in ein Reservoir abgeführt. Ebenso ist es bevorzugt, wenn das erste Volumen mit dem Reservoir für das hydraulische Medium verbunden wird, um eine mittels des Kolbenverdichters zu fördernde Menge an Medium zu erhöhen. Dies geht einher mit einer Reduzierung von Totraum im Zylinderkopf. Dabei wird benötigtes hydraulisches Medium (also um die Menge an hydraulischem Medium im zweiten Volumen zu erhöhen bzw. das zweite Volumen aufzufüllen) aus dem Reservoir zugeführt.For this purpose, the second volume is preferably connected to the first volume in order to reduce an amount of medium to be conveyed by means of the piston compressor. This goes hand in hand with an increase in dead space in the cylinder head. Excess hydraulic medium (that is to say in order to reduce hydraulic medium in the second volume) is for this purpose discharged from the first volume into a reservoir. It is also preferred if the first volume is connected to the reservoir for the hydraulic medium in order to increase an amount of medium to be conveyed by means of the piston compressor. This goes hand in hand with a reduction in dead space in the cylinder head. The required hydraulic medium (that is to say to increase the amount of hydraulic medium in the second volume or to fill the second volume) is supplied from the reservoir.

Je nach Bedarf kann also das zweite Volumen mit mehr oder weniger hydraulischem Medium befüllt werden. Da durch das hydraulische Medium im zweiten Volumen die Bewegung des Hubkolbens in Richtung unterer Totpunkt (also in Richtung des hydraulischen Antriebs) begrenzbar ist, kann so das Volumen, welches am Zylinderkopf bzw. am oberen Totpunkt zur Verdichtung zur Verfügung steht, verändert werden. Entsprechend kann das Verdichtungsverhältnis geändert werden.Depending on requirements, the second volume can therefore be filled with a more or less hydraulic medium. Since the movement of the reciprocating piston in the direction of bottom dead center (i.e. in the direction of the hydraulic drive) can be limited by the hydraulic medium in the second volume, the volume which is at the Cylinder head or at top dead center is available for compression, can be changed. Accordingly, the compression ratio can be changed.

Vorteilhafterweise wird als Kolbenverdichter ein mehrstufiger Kolbenverdichter mit wenigstens zwei Hubkolben und entsprechenden Zylindern verwendet. Eine Bewegung dieser Hubkolben in den entsprechenden Zylindern kann jedoch weiterhin mit dem einen hydraulischen Antrieb, dann mit entsprechend mehreren solcher erster Volumina, erfolgen. Es versteht sich, dass dann auch entsprechend mehrere solcher Dämpfungseinheiten vorgesehen sein können. Je nach Situation können die einzelnen Zylinder dann beispielsweise in Reihe oder sternförmig angeordnet werden. Die Verdichtung erfolgt dann derart, dass von einem Zylinder ausgestoßenes Medium einem anderen Zylinder zugeführt und dort weiter verdichtet wird.A multistage piston compressor with at least two reciprocating pistons and corresponding cylinders is advantageously used as the piston compressor. A movement of these reciprocating pistons in the corresponding cylinders can, however, still take place with the one hydraulic drive, then with a corresponding number of such first volumes. It goes without saying that a number of such damping units can then also be provided accordingly. Depending on the situation, the individual cylinders can then be arranged in a row or in a star shape, for example. The compression then takes place in such a way that medium ejected from one cylinder is fed to another cylinder and is further compressed there.

Besonders bevorzugt ist es, wenn eine ionische Flüssigkeit als Betriebsflüssigkeit [verwendet wird. In diesem Zusammenhang wird dann auch von einem sog. ionischen Verdichter gesprochen. Wie bereist eingangs erwähnt, bieten solche ionischen Verdichter Vorteile wie ein verringertes Totvolumen. Durch die hier vorgeschlagene Zu- bzw. Abfuhr von hydraulischem Medium können nun auch die verbleibenden Nachteile der Schallemission bzw. Bauteilabnutzung reduziert werden.It is particularly preferred when an ionic liquid is used as working fluid [is. In this context, what is known as an ionic compressor is also used. As already mentioned at the beginning, such ionic compressors offer advantages such as a reduced dead volume. The supply and discharge of hydraulic medium proposed here can now also reduce the remaining disadvantages of noise emission and component wear.

Gegenstand der Erfindung ist weiterhin ein Kolbenverdichter mit einem Hubkolben in einem Zylinder, wobei in dem Zylinder auf Seiten eines zu verdichtenden und zu fördernden Mediums ein Einlassventil und ein Auslassventil vorgesehen sind. Zudem weist der Kolbenverdichter einen hydraulischen Antrieb mit einem Hydraulikkolben auf, mittels dessen der Hubkolben unter Verwendung eines hydraulischen Mediums in einem ersten Volumen, mit dem der Hubkolben auf Seiten des hydraulischen Antriebs beaufschlagbar ist, hin und her bewegbar ist. Dabei ist wenigstens eine Messeinrichtung vorgesehen, mittels welcher eine Position des Hydraulikkolbens und/oder eines Drehwinkels einer zur Bewegung des Hydraulikkolbens vorgesehenen Welle und eine Position des Hubkolbens und/oder ein Druck im ersten Volumen ermittelbar sind. Der Kolbenverdichter ist nun dazu eingerichtet, bei Bedarf in Abhängigkeit von der Position des Hydraulikkolbens und/oder des Drehwinkels der zur Bewegung des Hydraulikkolbens vorgesehenen Welle in Relation zu der Position des Hubkolbens und/oder dem Druck im ersten Volumen hydraulisches Medium in das erste Volumen zuzuführen und/oder aus dem ersten Volumen abzuführen.The invention also relates to a piston compressor with a reciprocating piston in a cylinder, an inlet valve and an outlet valve being provided in the cylinder on the side of a medium to be compressed and conveyed. In addition, the piston compressor has a hydraulic drive with a hydraulic piston, by means of which the reciprocating piston can be moved back and forth using a hydraulic medium in a first volume with which the reciprocating piston can be acted upon on the hydraulic drive side. At least one measuring device is provided, by means of which a position of the hydraulic piston and / or an angle of rotation of a shaft provided for moving the hydraulic piston and a position of the reciprocating piston and / or a pressure in the first volume can be determined. The piston compressor is now set up to supply hydraulic medium into the first volume as required depending on the position of the hydraulic piston and / or the angle of rotation of the shaft provided for moving the hydraulic piston in relation to the position of the reciprocating piston and / or the pressure in the first volume and / or to be discharged from the first volume.

Vorzugsweise weist der Kolbenverdichter weiterhin eine hydraulische Dämpfungseinheit auf, mittels welcher unter Verwendung des hydraulischen Mediums und unter Bildung eines zweiten Volumens, das zumindest teilweise von dem Hubkolben begrenzt wird, eine Bewegung des Hubkolbens auf Seiten des hydraulischen Antriebs bei Bedarf begrenzbar ist. Vorteilhafterweise sind dabei ein erstes Ventil, mittels dessen das zweite Volumen mit dem ersten Volumen verbindbar ist, und ein zweites Ventil, mittels dessen hydraulisches Medium aus dem ersten Volumen in ein Reservoir für das hydraulische Medium abführbar ist, vorgesehen. Damit kann eine mittels des Kolbenverdichters zu fördernde Menge an Medium reduziert werden. Bevorzugt ist es auch, wenn ein drittes Ventil vorgesehen ist, mittels dessen das erste Volumen mit dem Reservoir für das hydraulische Medium verbindbar ist. Damit kann hydraulisches Medium dem ersten Volumen zugeführt werden. Dieses dritte Ventil kann vorzugsweise auch derart ausgebildet sein, dass automatisch hydraulisches Medium aus dem Reservoir dem ersten Volumen zuführbar ist, wenn auf Seiten des ersten Volumens ein geringerer Druck als auf Seiten des Reservoirs vorliegt. Das dritte Ventil kann hierzu beispielsweise als Rückschlagventil ausgebildet sein.The reciprocating compressor preferably also has a hydraulic damping unit by means of which a movement of the reciprocating piston on the hydraulic drive side can be limited if necessary using the hydraulic medium and forming a second volume which is at least partially limited by the reciprocating piston. A first valve, by means of which the second volume can be connected to the first volume, and a second valve, by means of which hydraulic medium can be discharged from the first volume into a reservoir for the hydraulic medium, are advantageously provided. In this way, an amount of medium to be conveyed by means of the piston compressor can be reduced. It is also preferred if a third valve is provided, by means of which the first volume can be connected to the reservoir for the hydraulic medium. Hydraulic medium can thus be fed to the first volume. This third valve can preferably also be designed in such a way that hydraulic medium can be automatically fed from the reservoir to the first volume when the pressure on the first volume side is lower than that on the reservoir side. For this purpose, the third valve can be designed, for example, as a check valve.

Der Kolbenverdichter ist vorteilhafterweise als mehrstufiger Kolbenverdichter mit wenigstens zwei Hubkolben und entsprechenden Zylindern ausgebildet. Zweckmäßigerweise ist in dem Kolbenverdichter eine ionische Flüssigkeit als Betriebsflüssigkeit vorgesehen.The piston compressor is advantageously designed as a multi-stage piston compressor with at least two reciprocating pistons and corresponding cylinders. An ionic liquid is expediently provided as the operating liquid in the reciprocating compressor.

Hinsichtlich der näheren Erläuterung sowie weiterer bevorzugter Ausgestaltungen und Vorteile des erfindungsgemäßen Kolbenverdichters sei zur Vermeidung von Wiederholungen auf obige Ausführungen zum erfindungsgemäßen Verfahren, das anhand eines Kolbenverdichters erläutert wird, verwiesen, die hier entsprechend gelten.With regard to the more detailed explanation as well as further preferred embodiments and advantages of the piston compressor according to the invention, reference is made to the above statements on the method according to the invention, which is explained using a piston compressor, to avoid repetition, which apply here accordingly.

Die Erfindung ist anhand eines Ausführungsbeispiels in der Zeichnung schematisch dargestellt und wird im Folgenden unter Bezugnahme auf die Zeichnung beschrieben.The invention is shown schematically in the drawing using an exemplary embodiment and is described below with reference to the drawing.

Kurze Beschreibung der Zeichnung

Figur 1
zeigt schematisch einen erfindungsgemäßen Kolbenverdichter in bevorzugter Ausführungsform, der sich zur Durchführung eines erfindungsgemäßen Verfahrens eignet.
Brief description of the drawing
Figure 1
shows schematically a piston compressor according to the invention in a preferred embodiment, which is suitable for carrying out a method according to the invention.

Ausführliche Beschreibung der ZeichnungDetailed description of the drawing

In Figur 1 ist schematisch ein erfindungsgemäßer Kolbenverdichter 100 in bevorzugter Ausführungsform dargestellt, der sich zur Durchführung eines erfindungsgemäßen Verfahrens eignet.In Figure 1 a piston compressor 100 according to the invention is shown schematically in a preferred embodiment, which is suitable for carrying out a method according to the invention.

Der Kolbenverdichter 100, in der gezeigten Form auch als Hubkolbenverdichter bezeichnet, umfasst hier einen Zylinder 110, in dem ein Hubkolben 111 hin und her bzw. auf und ab bewegt werden kann. An sich kann ein solcher Kolbenverdichter mehrstufig ausgebildet sein, d.h. mehrere der gezeigten Zylinder 110 mit Hubkolben 111 können vorhanden sein. Die folgende Beschreibung in Bezug auf den Zylinder mit Hubkolben gilt dann entsprechend auch für weitere Zylinder mit Hubkolben.The piston compressor 100, also referred to as a reciprocating compressor in the form shown, here comprises a cylinder 110 in which a reciprocating piston 111 can be moved back and forth or up and down. Such a reciprocating compressor can be designed in several stages, i.e. several of the cylinders 110 shown with reciprocating pistons 111 can be present. The following description in relation to the cylinder with reciprocating piston then also applies accordingly to other cylinders with reciprocating pistons.

Der Kolbenverdichter 100 wird durch einen Hydraulikantrieb bzw. einen hydraulischen Antrieb angetrieben, welcher hier einen Hydraulikkolben 120 umfasst. Der Hydraulikkolben 120 wird von einem Umlaufrad mit Welle 121 mit geeignetem Gestänge (Hydraulikkurbeltrieb) angetrieben. Durch eine Drehung dieser Welle 121, wie mit einem Pfeil angedeutet, führt durch die Verwendung von hydraulischem Medium a (Hydrauliköl) in einem ersten Volumen 141 zu einer Auf- und Abbewegung des Hubkolbens 110, wie ebenfalls mit einem Pfeil angedeutet. Der Hubkolben 111 oszilliert im Zylinder 110 zwischen zwei Umkehrpunkten, die als unterer Totpunkt (UT) und oberer Totpunkt (OT) bezeichnet werden.The piston compressor 100 is driven by a hydraulic drive or a hydraulic drive, which here comprises a hydraulic piston 120. The hydraulic piston 120 is driven by a planet wheel with a shaft 121 with a suitable linkage (hydraulic crank drive). By rotating this shaft 121, as indicated by an arrow, the use of hydraulic medium a (hydraulic oil) in a first volume 141 results in an up and down movement of the reciprocating piston 110, as also indicated by an arrow. The reciprocating piston 111 oscillates in the cylinder 110 between two reversal points, which are referred to as bottom dead center (BDC) and top dead center (TDC).

Die Frequenz, mit welcher sich die Welle dreht und sich entsprechend der Hubkolben auf und ab bewegt, kann beispielsweise zwischen 0,5 Hz und 12 Hz liegen (wird jedoch in der Regel konstant gehalten), der Hub des Hubkolbens kann beispielsweise zwischen 30mm und 100mm liegen. Der Hub bzw. das Hubvolumen des Hydraulikkolbens ist in der Regel ebenfalls konstant.The frequency at which the shaft rotates and the reciprocating piston moves up and down, for example, can be between 0.5 Hz and 12 Hz (but is usually kept constant), the stroke of the reciprocating piston can for example be between 30mm and 100mm lie. The stroke or the stroke volume of the hydraulic piston is usually also constant.

Das hydraulische Medium a wird hier also an die Bodenseite des Hubkolbens 111 gefördert. Der Hubkolben 111 wird dabei entsprechend nach oben bewegt und verdichtet ein Zwei-Phasengemisch im sog. Gaszylinder 114, also dem oberen Bereich des Zylinders Dieses Zwei-Phasengemisch umfasst hier einerseits ein zu verdichtendes und zu förderndes Medium b und andererseits eine ionische Betriebsflüssigkeit. Überschreitet der Druck im Zylinder 110 den Gegendruck am Druckventil bzw. Auslassventil 113, wird dieses geöffnet und das Medium b annähernd isobar in den Druckbereich gefördert, bis der obere Totpunkt erreicht ist.The hydraulic medium a is thus conveyed to the bottom side of the reciprocating piston 111 here. The reciprocating piston 111 is accordingly moved upwards and compresses a two-phase mixture in the so-called gas cylinder 114, that is to say the upper region of the cylinder. This two-phase mixture here comprises, on the one hand, a medium b to be compressed and conveyed and, on the other hand, an ionic operating fluid. If the pressure in the cylinder 110 exceeds the counter pressure at the pressure valve or outlet valve 113, this is opened and the medium b is conveyed approximately isobarically into the pressure range until the top dead center is reached.

Sobald sich der Hydraulikkolben 120 nach unten bewegt, wird der Gegendruck im Zylinder 110 unterschritten und das Auslassventil 113 geschlossen. Der sich nach unten bewegende Hubkolben 111 verringert den Druck im Zylinder 110 bis der anliegende Druck am Saugventil bzw. Einlassventil 112 unter das Niveau im Saugbereich sinkt.As soon as the hydraulic piston 120 moves downwards, the counterpressure in the cylinder 110 falls below the level and the outlet valve 113 is closed. The downward moving piston 111 reduces the pressure in the cylinder 110 until the pressure applied to the suction valve or inlet valve 112 falls below the level in the suction area.

Je weniger Restvolumen bzw. Totraum besteht, umso früher kann das Einlassventil 112 öffnen und proportional dazu die angesaugte Menge erhöht werden. Systembedingt kann die Stellung des Hubkolbens 111 von der Hubstellung des Hydraulikkolbens 120 abweichen. Die Leckage-behaftete Verdichtung im Hydraulikantrieb führt dazu, dass in weiterer Folge das am Hydraulikkolben 120 vorbeigeleitete hydraulische Medium a zunächst in ein Reservoir 130 (bzw. einen Tank) gelangt.The less residual volume or dead space there is, the earlier the inlet valve 112 can open and the quantity sucked in can be increased proportionally thereto. As a result of the system, the position of the reciprocating piston 111 can deviate from the stroke position of the hydraulic piston 120. The leakage-prone compression in the hydraulic drive leads to the fact that the hydraulic medium a, which has bypassed the hydraulic piston 120, first reaches a reservoir 130 (or a tank).

Von dort kann es über eine Pumpe 131 und einen Wärmetauscher 132 und schließlich ein Rückschlagventil 153 wieder in den Hydraulikkreis bzw. das erste Volumen 141 zurückgefördert werden, um die Stellungsabweichungen zwischen Hydraulikkolben 120 und Hubkolben 111 zu kompensieren.From there it can be fed back into the hydraulic circuit or the first volume 141 via a pump 131 and a heat exchanger 132 and finally a check valve 153 in order to compensate for the positional deviations between hydraulic piston 120 and reciprocating piston 111.

Die benötigte Menge kann nun im Rahmen der vorliegenden Erfindung beispielsweise über einen Datenabgleich zwischen einer Messeinrichtung 161 (beispielsweise ein Wegmesssystem) und einer Messeinrichtung 160 (beispielsweise ein Drehwinkelaufnehmer) berechnet und korrigiert werden. Während mittels der Messeinrichtung 161 beispielsweise die Position x des Hubkolbens 111 ermittelt werden kann, kann mit der Messeinrichtung 160 beispielsweise ein Drehwinkel ϕ der Welle 121 ermittelt werden. Zudem kann mittels einer geeigneten Messeinrichtung 162 beispielsweise auch ein Druck p im ersten Volumen 141 erfasst werden.The required amount can now be calculated and corrected within the scope of the present invention, for example via a data comparison between a measuring device 161 (for example a displacement measuring system) and a measuring device 160 (for example a rotation angle sensor). While the position x of the reciprocating piston 111 can be determined by means of the measuring device 161, for example, a rotational angle ϕ of the shaft 121 can be determined with the measuring device 160. In addition, a pressure p in the first volume 141 can also be recorded, for example, by means of a suitable measuring device 162.

Ein Anschlagen des Hubkolbens 111 am Zylinderkopf wird nun durch eine Drucküberhöhung am Ende der eigentlich isobaren Ausschiebephase erkannt, wodurch das überschüssige hydraulische Medium über ein Druckbegrenzer-Ventil 154 wieder zurück in das Reservoir 130 gefördert wird.A strike of the reciprocating piston 111 on the cylinder head is now recognized by an increase in pressure at the end of the actually isobaric expulsion phase, as a result of which the excess hydraulic medium is conveyed back into the reservoir 130 via a pressure limiter valve 154.

Mechanischer Kontakt des Hubkolbens 111 am Kolben- bzw. Zylinderboden wird durch eine Druckunterschreitung während der Einströmphase erkannt. Hier wird die fehlende Menge an hydraulischem Medium über das Rückschlagventil 153 (das im Rahmen der Erfindung auch als drittes Ventil bezeichnet wird) gezogen bzw. zugeführt, um den Hubkolben 111 in den Normbereich zu bewegen.Mechanical contact of the reciprocating piston 111 on the piston or cylinder base is detected when the pressure falls below the limit during the inflow phase. Here, the missing amount of hydraulic medium is drawn or supplied via the check valve 153 (which is also referred to as the third valve in the context of the invention) in order to move the reciprocating piston 111 into the normal range.

Indem nun also beispielsweise eine Druckmessung in dem ersten Volumen in Abhängigkeit von dem Drehwinkel der Welle 121 vorgenommen wird, kann erkannt werden, wenn ein Anschlag des Hubkolbens 111 am Zylinderkopf oder Zylinderboden auftritt oder bevorsteht, und es kann, beispielsweise durch geeignete Ansteuerung der Ventile 153 bzw. 154 hydraulisches Medium ab- oder zugeführt werdenBy now, for example, taking a pressure measurement in the first volume as a function of the angle of rotation of the shaft 121, it can be recognized when a stop of the reciprocating piston 111 on the cylinder head or cylinder base occurs or is imminent, and this can be done, for example, by suitable control of the valves 153 or 154 hydraulic medium can be discharged or supplied

Weiterhin ist eine Dämpfungseinheit 140 vorgesehen, mittels welcher ein adaptives Dämpfungssystem verwirklicht werden kann, und zwar unabhängig von der Frequenz, von den Druckverhältnissen im Kolbenverdichter und von der Leckage im Hydraulikbereich. Diese Dämpfungseinheit 140 kann dazu verwendet werden, die Bewegung des Hubkolbens 111 nach unten zu dämpfen und somit die Schallemissionen und mechanischen Belastungen während der Bewegung in Richtung unterer Totpunkt zu verringern.Furthermore, a damping unit 140 is provided, by means of which an adaptive damping system can be implemented, regardless of the frequency, of the pressure conditions in the piston compressor and of the leakage in the hydraulic area. This damping unit 140 can be used to dampen the downward movement of the reciprocating piston 111 and thus to reduce the noise emissions and mechanical loads during the movement in the direction of bottom dead center.

Wird über die drehwinkelaufgelöste Druckmessung im Hydrauliksystem, also hier im ersten Volumen 141, eine Leckage im Ölkreislauf, also hier auch in dem ersten Volumen 141, detektiert, kann dies kompensiert werden. Zudem ist es möglich, durch das adaptive Dämpfungssystem den oberen sowie den unteren Totpunkt und damit das Verdichtungsverhältnis bzw. die geförderte Menge an Medium einzustellen. Hierzu wird je nach Bedarf bzw. Anforderung an die geforderte Menge zusätzliches hydraulisches Medium zugeführt bzw. überschüssiges hydraulisches Medium in das Reservoir abgeführt bzw. zurückgeschoben.If a leakage in the oil circuit, ie here also in the first volume 141, is detected via the pressure measurement resolved by the angle of rotation in the hydraulic system, that is to say here in the first volume 141, this can be compensated. It is also possible to use the adaptive damping system to set the upper and lower dead center and thus the compression ratio or the amount of medium conveyed. For this purpose, depending on the need or requirement of the required amount, additional hydraulic medium is supplied or excess hydraulic medium is discharged into the reservoir or pushed back.

Soll die geförderte Menge vergrößert bzw. der vorhandene Totraum verkleinert werden, so wird ein erstes Ventil 150 geschlossen. Dadurch wird der Hubkolben 111 an der Bewegung in Richtung unterer Totpunkt bzw. in Richtung hydraulischem Antrieb gehindert, obwohl sich der Hydraulikkolben 120 nach unten bewegt. Dadurch wird die benötigte Menge an hydraulischem Medium durch den in Folge entstehenden Unterdruck über das Rückschlagventil 153 in den Kreislauf bzw. in das erste Volumen 141 gesaugt. Bewegt sich der Hydraulikkolben 120 wieder nach oben, ist das System geschlossen und der Hubkolben 111 wurde um ein definiertes Volumen (durch die zusätzlich geführte Menge an hydraulischem Medium) angehoben, wodurch der Totraum verringert und die geförderte Menge an zu verdichtendem Medium vergrößert wird.If the conveyed quantity is to be increased or the existing dead space is to be reduced, a first valve 150 is closed. As a result, the reciprocating piston 111 is prevented from moving in the direction of bottom dead center or in the direction of the hydraulic drive, although the hydraulic piston 120 is moving downward. As a result, the required amount of hydraulic medium is sucked into the circuit or into the first volume 141 via the non-return valve 153 as a result of the negative pressure that occurs. If the hydraulic piston 120 moves upwards again, the system is closed and the reciprocating piston 111 has been raised by a defined volume (due to the additional amount of hydraulic medium carried), whereby the dead space is reduced and the conveyed amount of medium to be compressed is increased.

Wird die Menge an hydraulischem Medium zu stark angehoben und der Hubkolben 111 droht, mit dem Zylinderkopf zu kollidieren, so kann das dritte Ventil 155 geöffnet und Füllmenge abgebaut werden.If the amount of hydraulic medium is increased too much and the reciprocating piston 111 threatens to collide with the cylinder head, the third valve 155 can be opened and the filling amount reduced.

Soll die geförderte Menge verringert bzw. der vorhandene Totraum vergrößert werden, so wird das erste Ventil 150 geöffnet, um die Abwärtsbewegung des Hubkolbens 111 nicht zu beeinflussen. Gleichzeitig wird das zweite Ventil 155 geöffnet, um eine definierte Menge an hydraulischem Medium abzubauen bzw. abzuführen, was durch die Bewegung des Hydraulikkolbens 120 nach oben erfolgt. Ist die geforderte Position des Hubkolbens erreicht, so kann das erste Ventil 150 wieder geschlossen werden.If the conveyed quantity is to be reduced or the existing dead space is to be increased, the first valve 150 is opened so as not to influence the downward movement of the reciprocating piston 111. At the same time, the second valve 155 is opened in order to reduce or discharge a defined amount of hydraulic medium, which takes place through the movement of the hydraulic piston 120 upwards. Once the required position of the reciprocating piston has been reached, the first valve 150 can be closed again.

Erfolgt dies vor Erreichen des unteren Totpunkts durch den Hydraulikkolben 120, so fördert dieser über das Rückschlagventil 153 die nötige Menge an hydraulischem Medium nach.If this is done by the hydraulic piston 120 before the bottom dead center is reached, the latter delivers the necessary amount of hydraulic medium via the check valve 153.

Diese Einstellungen können in einem Regelkreis durch mehrmalige Iteration an den geforderten Betriebspunkt angenähert werden. Wird eine Änderung der Zwischenkreisdrücke der einzelnen Stufen gefordert (also bei einem mehrstufigen Kolbenverdichter), so kann dies auf die gleiche Art wie eben beschrieben, erfolgen. Es wird lediglich der Druck als Regelgröße herangezogen und im Kreis mit den anderen Stufen abgeglichen.These settings can be approximated to the required operating point in a control loop by repeated iteration. If a change in the intermediate circuit pressures of the individual stages is required (i.e. in the case of a multi-stage piston compressor), this can be done in the same way as just described. Only the pressure is used as a control variable and compared in a circle with the other stages.

Wurde ein Betriebspunkt eingestellt, so ist eine Änderung des Drucks im System direkt proportional zur Stellung des Hubkolbens 111. Eine Abweichung der Position der dem Drehwinkel ϕ der Welle 121 zugeordneten Position x des Hubkolbens 111 aufgrund von Leckage kann durch Blockieren des Hubkolbens 111 mittels der Dämpfungseinheit 140 erfolgen, es wird hydraulisches Medium über das Rückschlagventil 153 nachgefördert und die Fehlstellung kompensiert.If an operating point has been set, a change in the pressure in the system is directly proportional to the position of the reciprocating piston 111. A deviation in the position x of the reciprocating piston 111 assigned to the angle of rotation ϕ of the shaft 121 due to leakage can be caused by the blocking of the reciprocating piston 111 by means of the damping unit 140, hydraulic medium is replenished via the check valve 153 and the misalignment is compensated.

Dieses adaptive Dämpfungssystem erlaubt es, hydraulisch angetriebene Kolbenverdichter hinsichtlich des nutzbaren Hubvolumens zu optimieren. Es wird ermöglicht, den Kolbenweg variabel zu gestalten und je nach Anforderung an das System bzgl. Fördermenge, Druck und Effektivität zu optimieren.This adaptive damping system makes it possible to optimize hydraulically driven piston compressors with regard to the usable stroke volume. It is possible to make the piston travel variable and, depending on the requirements of the system, to optimize it in terms of delivery rate, pressure and effectiveness.

Das Restvolumen zwischen Hubkolben und Zylinderkopf, der sogenannte Totraum, expandiert bei der Abwärtsbewegung des Hubkolbens und beeinflusst je nach Größe den Öffnungszeitpunkt des in der Regel Feder-betätigten Saugventils. Je größer der Totraum ist, desto später öffnet dieses und umso weniger Fördermenge kann angesaugt werden.The remaining volume between the reciprocating piston and the cylinder head, the so-called dead space, expands when the reciprocating piston moves downwards and, depending on its size, influences the opening time of the normally spring-operated suction valve. The larger the dead space, the later it opens and the less flow rate that can be sucked in.

Dies beeinflusst direkt die Effizienz der jeweiligen Verdichterstufe. In Abstimmung mit den restlichen Stufen kann somit eine Anpassung der Zwischenkreisdrücke erfolgen, was in bestimmten Betriebsbereichen erforderlich sein kann. Somit ist es möglich, mit dem vorgeschlagenen Verfahren bzw. dem Kolbenverdichter eine große Variabilität hinsichtlich der benötigten Fördermenge sowie der anliegenden Drücke im Zwischenkreis zu realisieren.This directly influences the efficiency of the respective compressor stage. In coordination with the remaining stages, the intermediate circuit pressures can thus be adapted, which may be necessary in certain operating ranges. It is thus possible to use the proposed method or the piston compressor to achieve great variability in terms of the required delivery rate and the pressures applied in the intermediate circuit.

Durch die Möglichkeit der Dämpfung des Hubkolbens sowie der Huboptimierung ist es möglich, dauerhaft mechanische Belastungen zu reduzieren, was einerseits zu einer Erhöhung der möglichen Standzeit der Verdichterkomponenten führt, und es andererseits erlaubt, Werkstoffe zu verwenden, die eine geringere Güte besitzen und dadurch einen größeren Freiraum hinsichtlich der Kostenoptimierung bzgl. Rohmaterial und Fertigungskosten bietet.The possibility of damping the reciprocating piston and optimizing the stroke makes it possible to permanently reduce mechanical loads, which on the one hand leads to an increase in the possible service life of the compressor components and on the other hand makes it possible to use materials that have a lower quality and therefore a higher one Offers freedom in terms of cost optimization with regard to raw material and manufacturing costs.

Mit erwähnten Effekten einher geht die Absenkung der Schwingungen und Geräuschemissionen, wodurch auch Einsparungen getroffen werden können hinsichtlich bisher notwendiger Dämmungsmaßnahmen und folglich der Betrieb beispielsweise eines Tankstellensystems (in dem mit einem solchen Kolbenverdichter beispielsweise Wasserstoff verdichtet wird) in Wohnraumumgebung erleichtert werden kann.The effects mentioned are accompanied by a reduction in vibrations and noise emissions, which means that savings can also be made with regard to previously necessary insulation measures and consequently operation For example, a filling station system (in which such a reciprocating compressor is used to compress hydrogen, for example) can be facilitated in a living space environment.

Durch die beschriebene Konfiguration ist ein solcher Kolbenverdichter sehr variabel und vereinfacht dadurch die Anwendung eines Baukastensystems, auch hinsichtlich unterschiedlicher Betriebsmedien, Grenzwerten und Anforderungen und erlaubt somit eine einfachere Serienfertigung aufgrund der nun möglichen Baugleichheit der einzelnen Komponenten trotz unterschiedlicher Anwendung.Due to the configuration described, such a reciprocating compressor is very variable and thus simplifies the use of a modular system, also with regard to different operating media, limit values and requirements and thus allows easier series production due to the identical construction of the individual components now possible despite different applications.

Eine Erweiterung bestehender bzw. bereits ausgelieferter Kolbenverdichter zu einem vorgeschlagenen Kolbenverdichter erlaubt die Optimierung der Betriebsparameter sowie eine Effizienzsteigerung. Zudem ist es möglich, bestehende Standzeiten zu erhöhen und Schwingungen und Schallemissionen zu verringern.An extension of an existing or already delivered piston compressor to a proposed piston compressor allows the optimization of the operating parameters and an increase in efficiency. It is also possible to increase existing service life and reduce vibrations and noise emissions.

Die Einbindung in ein bestehendes System (also einen bestehenden Kolbenverdichter oder mehrere davon) kann im Zuge eines regelmäßigen Wartungsvorgangs durchgeführt werden. Hierzu können zusätzlich ein Wegmesssystem und ein Drehwinkelgeber (im Sinne der erwähnten Messeinrichtungen) angebracht und die Automatisierungsprogrammierung der Anlage um die notwendigen Steuerungsroutinen erweitert werden.The integration into an existing system (i.e. an existing reciprocating compressor or several of them) can be carried out as part of a regular maintenance process. For this purpose, a position measuring system and a rotary encoder (in the sense of the mentioned measuring devices) can be attached and the automation programming of the system can be expanded to include the necessary control routines.

Eine weitere Ausgestaltung besteht darin, dass es in Verbindung mit steuerbaren Saug- und Druckventilen beispielsweise auf piezoelektrischer Basis, wie sie beispielsweise in Automotive-Anwendungen Verwendung finden, möglich ist, ein Expandersystem zu realisieren. Ein solches nutzt die Expansionsarbeit bei der Entspannung des Gases beispielsweise in einem Dispensersystem, bei welchem Gas eines niedrigeren Druckniveaus benötigt wird, und kann dadurch auf Basis eines Energierückgewinnungssystems zur Stromerzeugung dienen.Another embodiment consists in the fact that it is possible to implement an expander system in connection with controllable suction and pressure valves, for example on a piezoelectric basis, as they are used, for example, in automotive applications. Such a system uses the expansion work during the expansion of the gas, for example in a dispenser system, in which gas at a lower pressure level is required, and can thus be used to generate electricity on the basis of an energy recovery system.

Claims (10)

  1. Method for operating a piston compressor (100) having a reciprocating piston (111) in a cylinder (110), an inlet valve (112) and an outlet valve (113) being provided in the cylinder (110) on the side of a medium (b) to be compressed and conveyed,
    the reciprocating piston (111) being moved back and forth by way of a hydraulic drive (120, 121) with a hydraulic piston (120) using a hydraulic medium (a) in a first volume (141), with which the reciprocating piston (111) is loaded on the side of the hydraulic drive (120, 121),
    characterized in that hydraulic medium (a) is supplied into the first volume (141) and/or discharged from the first volume (141) as required depending on a position of the hydraulic piston (120) and/or a rotational angle (ϕ) of a shaft (121) provided for moving the hydraulic piston (120) in relation to a position (x) of the reciprocating piston (111) and/or a pressure (p) in the first volume (141).
  2. Method according to Claim 1, wherein a movement of the reciprocating piston (111) is limited as required on the side of the hydraulic drive (120, 121) by way of a hydraulic damping unit (140) using the hydraulic medium (a) and forming a second volume (142) which is at least partially delimited by the reciprocating piston (111).
  3. Method according to Claim 2, wherein the second volume (142) is connected to the first volume (141) in order to reduce an amount of medium (b) to be conveyed by means of the piston compressor (100), wherein excess hydraulic medium (a) is discharged from the first volume (141) into a reservoir (130), and/or
    wherein the first volume (141) is connected to the reservoir (130) for the hydraulic medium in order to increase an amount of medium (b) to be conveyed by means of the piston compressor (100), wherein required hydraulic medium is supplied from the reservoir (130).
  4. Method according to any one of the preceding claims, wherein a multi-stage piston compressor with at least two reciprocating pistons and corresponding cylinders is used as the piston compressor (100).
  5. Method according to any one of the preceding claims, wherein an ionic liquid is used as the working liquid.
  6. Piston compressor (100) having a reciprocating piston (111) in a cylinder (110), an inlet valve (112) and an outlet valve (113) being provided in the cylinder (110) on the side of a medium (b) to be compressed and conveyed,
    having a hydraulic drive (120, 121) with a hydraulic piston (120), by means of which the reciprocating piston (111) can be moved back and forth using a hydraulic medium (a) in a first volume (141), with which the reciprocating piston (111) can be loaded on the side of the hydraulic drive (120, 121),
    characterized by at least one measuring device (160, 161, 162), by means of which a position of the hydraulic piston (111) and/or a rotational angle (ϕ) of a shaft (121) provided for moving the hydraulic piston (120) and a position of the reciprocating piston (x) and/or a pressure (p) in the first volume (141) can be determined,
    wherein the piston compressor (100) is designed to supply hydraulic medium (a) into the first volume (141) and/or to discharge it from the first volume (141) as required depending on the position of the hydraulic piston (120) and/or the rotational angle (ϕ) of the shaft (121) provided for moving the hydraulic piston (120) in relation to the position (x) of the reciprocating piston (111) and/or the pressure (p) in the first volume (141).
  7. Piston compressor (100) according to Claim 6, furthermore having a hydraulic damping unit (140) by means of which a movement of the reciprocating piston (111) can be limited as required on the side of the hydraulic drive (120, 121) using the hydraulic medium (a) and forming a second volume (142) which is at least partially delimited by the reciprocating piston (111).
  8. Piston compressor (100) according to Claim 7, having a first valve (150), by means of which the second volume (142) can be connected to the first volume (141), and having a second valve (155), by means of which hydraulic medium (a) can be discharged from the first volume (141) into a reservoir (130) for the hydraulic medium, and/or
    having a third valve (153), by means of which the first volume (141) can be connected to the reservoir (130) for the hydraulic medium.
  9. Piston compressor (100) according to any one of Claims 6 to 8, which is designed as a multi-stage piston compressor with at least two reciprocating pistons and corresponding cylinders.
  10. Piston compressor (100) according to any one of Claims 6 to 8, in which an ionic liquid is provided as the working liquid.
EP18803317.9A 2017-11-22 2018-11-06 Method for operating a piston compressor and piston compressor Active EP3714162B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017010789.0A DE102017010789A1 (en) 2017-11-22 2017-11-22 Method for operating a reciprocating compressor and reciprocating compressor
PCT/EP2018/025281 WO2019101361A1 (en) 2017-11-22 2018-11-06 Method for operating a piston compressor, and piston compressor

Publications (2)

Publication Number Publication Date
EP3714162A1 EP3714162A1 (en) 2020-09-30
EP3714162B1 true EP3714162B1 (en) 2021-09-22

Family

ID=64308690

Family Applications (1)

Application Number Title Priority Date Filing Date
EP18803317.9A Active EP3714162B1 (en) 2017-11-22 2018-11-06 Method for operating a piston compressor and piston compressor

Country Status (9)

Country Link
US (1) US11828281B2 (en)
EP (1) EP3714162B1 (en)
JP (1) JP7198818B2 (en)
KR (1) KR102602056B1 (en)
CN (1) CN111512044B (en)
DE (1) DE102017010789A1 (en)
DK (1) DK3714162T3 (en)
HU (1) HUE057095T2 (en)
WO (1) WO2019101361A1 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113107812B (en) * 2021-04-30 2022-08-30 重庆市南川区金鑫纸业有限公司 Vacuum system dewatering device for papermaking
CN115681073B (en) * 2022-10-14 2023-11-14 西安交通大学 T-shaped wedge type ionic liquid compressor and liquid drive control mode thereof

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3787397B2 (en) * 1996-11-11 2006-06-21 株式会社三共製作所 Pressure loss compensation device for fluid pressure circuit and cam device provided with the same
AT3213U1 (en) * 1998-03-11 1999-11-25 Hoerbiger Ventilwerke Gmbh DAMAGE ADJUSTMENT DEVICE FOR PISTON COMPRESSORS
JP2006170097A (en) * 2004-12-16 2006-06-29 Toyota Motor Corp Fuel pump
DE102007033601B3 (en) * 2007-07-17 2008-11-13 Compart Compressor Technology Gmbh & Co. Kg Device for stepless regulation of the dead space volume of a reciprocating compressor
DE102010053091A1 (en) * 2010-12-01 2012-06-06 Linde Aktiengesellschaft Multi-stage piston compressor
DE102011105824B3 (en) * 2011-05-27 2012-05-31 Fresenius Medical Care Deutschland Gmbh Method for determination of air in e.g. blood, involves detecting operational parameters of pump, and determining gas concentration from operational parameters under consideration of system compressibility in pump
FR3020840B1 (en) * 2014-05-12 2017-03-03 Vianney Rabhi LIMIT SWITCH FOR PISTON PRESSURE CONVERTER
JP6362008B2 (en) * 2015-02-09 2018-07-25 Smc株式会社 Pump system and pump abnormality detection method
GB201601602D0 (en) 2016-01-28 2016-03-16 Linde Ag An apparatus and method for compressing fluid
US20180372083A1 (en) * 2017-06-22 2018-12-27 Wanner Engineering, Inc. Hydraulic diaphragm control

Also Published As

Publication number Publication date
EP3714162A1 (en) 2020-09-30
US11828281B2 (en) 2023-11-28
JP7198818B2 (en) 2023-01-04
KR20200108823A (en) 2020-09-21
HUE057095T2 (en) 2022-04-28
DE102017010789A1 (en) 2019-05-23
CN111512044A (en) 2020-08-07
KR102602056B1 (en) 2023-11-13
WO2019101361A1 (en) 2019-05-31
JP2021504619A (en) 2021-02-15
DK3714162T3 (en) 2021-11-22
US20200309116A1 (en) 2020-10-01
CN111512044B (en) 2022-11-18

Similar Documents

Publication Publication Date Title
EP2354475B1 (en) Method for operating a piston expander of a steam motor
DE69227925T2 (en) HYDRAULIC PILE FRAME
DE102016113882A1 (en) Electro-hydrostatic drive system
EP3714162B1 (en) Method for operating a piston compressor and piston compressor
WO2014048418A1 (en) Method and device for actuating an electrically commutated fluid working machine
DE102016009416A1 (en) Energy-efficient press with stable ram guide
WO2006037671A1 (en) Radial piston pump
EP1599668B1 (en) Fuel injection device for an internal combustion engine
EP1564414B1 (en) Hydraulic drive
WO2021013670A1 (en) Valve device for a reciprocating-piston compressor
DE19804374B4 (en) Axial piston machine with medium pressure opening
EP1998045A1 (en) Displacement machine with coaxial valves
EP3652417B1 (en) Method and device for expanding a gas with a reciprocating-piston machine
DE102013007668B4 (en) Hydraulic drive system for two cylinders arranged approximately parallel
DE102007002729B3 (en) Fuel pump for high pressure fuel injection system i.e. common rail injection system, has valve arranged in housing at highest position with smallest opening pressure and other valves arranged at lowest position with largest opening pressure
DE19902259A1 (en) Assembly process
EP2791505B1 (en) Pressure intensifier, method of operating a pressure intensifier, and use of a pressure intensifier
DE102005060957B4 (en) High pressure pump with several pistons per cylinder
DE102018201742A1 (en) Fuel delivery device for cryogenic fuels
EP1798415B1 (en) High pressure pump
EP3084212B1 (en) Conveying device for a fluid
DE19823086C2 (en) Valve control for fluid-powered, flywheel-less reciprocating machine
DE102017103091B4 (en) machine press
WO2014096175A1 (en) High pressure pump
DE102013215953A1 (en) high pressure pump

Legal Events

Date Code Title Description
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: UNKNOWN

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE

PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20200430

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

DAV Request for validation of the european patent (deleted)
DAX Request for extension of the european patent (deleted)
REG Reference to a national code

Ref country code: DE

Ref legal event code: R079

Ref document number: 502018007199

Country of ref document: DE

Free format text: PREVIOUS MAIN CLASS: F04B0025000000

Ipc: F04B0009100000

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

RIC1 Information provided on ipc code assigned before grant

Ipc: F04B 35/04 20060101ALI20210330BHEP

Ipc: F04B 49/16 20060101ALI20210330BHEP

Ipc: F04B 9/10 20060101AFI20210330BHEP

INTG Intention to grant announced

Effective date: 20210416

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502018007199

Country of ref document: DE

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

Ref country code: AT

Ref legal event code: REF

Ref document number: 1432526

Country of ref document: AT

Kind code of ref document: T

Effective date: 20211015

REG Reference to a national code

Ref country code: DK

Ref legal event code: T3

Effective date: 20211119

REG Reference to a national code

Ref country code: NL

Ref legal event code: FP

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG9D

REG Reference to a national code

Ref country code: NO

Ref legal event code: T2

Effective date: 20210922

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210922

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210922

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210922

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210922

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20211222

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210922

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210922

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20211223

REG Reference to a national code

Ref country code: HU

Ref legal event code: AG4A

Ref document number: E057095

Country of ref document: HU

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20220122

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210922

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210922

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20220124

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210922

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210922

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210922

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210922

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210922

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502018007199

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210922

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20211106

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20220623

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20211106

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210922

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210922

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20221106

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210922

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20221106

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210922

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210922

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NL

Payment date: 20241120

Year of fee payment: 7

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: HU

Payment date: 20241030

Year of fee payment: 7

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20241119

Year of fee payment: 7

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NO

Payment date: 20241119

Year of fee payment: 7

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DK

Payment date: 20241120

Year of fee payment: 7

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: BE

Payment date: 20241119

Year of fee payment: 7

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20241128

Year of fee payment: 7

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 20241118

Year of fee payment: 7

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20241129

Year of fee payment: 7

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CH

Payment date: 20241201

Year of fee payment: 7