EP3714162B1 - Procédé de fonctionnement d' un compresseur à piston et compresseur à piston - Google Patents

Procédé de fonctionnement d' un compresseur à piston et compresseur à piston Download PDF

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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
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EP
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Prior art keywords
piston
hydraulic
volume
medium
reciprocating
Prior art date
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EP18803317.9A
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German (de)
English (en)
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EP3714162A1 (fr
Inventor
Sascha Dorner
Christoph Nagl
Johannes FRITZER
Klaus Fischer
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Linde GmbH
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Linde GmbH
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • 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
    • 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
    • F04B39/10—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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/12—Kind or type gaseous, i.e. compressible
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/96—Preventing, counteracting or reducing vibration or noise

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.

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  • 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)

Claims (10)

  1. Procédé pour le fonctionnement d'un compresseur à piston (100) présentant un piston alternatif (111) dans un cylindre (110), une soupape d'entrée (112) et une soupape de sortie (113) étant disposées dans le cylindre (110) sur le côté d'un fluide (b) à comprimer et à acheminer,
    un entraînement hydraulique (120, 121) pourvu d'un piston hydraulique (120) animant le piston alternatif (111) d'un mouvement de va-et-vient à l'aide d'un fluide hydraulique (a) dans un premier volume (141), qui sollicite le piston alternatif (111) sur le côté de l'entraînement hydraulique (120, 121),
    caractérisé en ce que, si nécessaire, en fonction d'une position du piston hydraulique (120) et/ou d'un angle de rotation (ϕ) d'un arbre (121) destiné au déplacement du piston hydraulique (120) en relation avec une position (x) du piston alternatif (111) et/ou une pression (p) dans le premier volume (141), du fluide hydraulique (a) est introduit dans le premier volume (141) et/ou évacué du premier volume (141).
  2. Procédé selon la revendication 1, une unité d'amortissement hydraulique (140) limitant, si nécessaire, à l'aide du fluide hydraulique (a) et en formant un deuxième volume (142), qui est limité au moins partiellement par le piston alternatif (111), un déplacement du piston alternatif (111) du côté de l'entraînement hydraulique (120, 121).
  3. Procédé selon la revendication 2, le deuxième volume (142) étant relié au premier volume (141) pour réduire une quantité de fluide (b) à acheminer au moyen du compresseur à piston (100), le fluide hydraulique (a) en excès étant évacué du premier volume (141) dans un réservoir (130) et/ou
    le premier volume (141) étant relié au réservoir (130) pour le fluide hydraulique pour augmenter une quantité de fluide (b) à acheminer au moyen du compresseur à piston (100), le fluide hydraulique nécessaire étant alimenté à partir du réservoir (130).
  4. Procédé selon l'une quelconque des revendications précédentes, un compresseur à piston à plusieurs étages présentant au moins deux pistons alternatifs et des cylindres correspondants étant utilisé comme compresseur à piston (100).
  5. Procédé selon l'une quelconque des revendications précédentes, un liquide ionique étant utilisé comme liquide de fonctionnement.
  6. Compresseur à piston (100) présentant un piston alternatif (111) dans un cylindre (110), une soupape d'entrée (112) et une soupape de sortie (113) étant disposées dans le cylindre (110) sur le côté d'un fluide (b) à comprimer et à acheminer,
    présentant un entraînement hydraulique (120, 121) pourvu d'un piston hydraulique (120) au moyen duquel le piston alternatif (111) peut être animé d'un mouvement de va-et-vient à l'aide d'un fluide hydraulique (a) dans un premier volume (141), qui peut solliciter le piston alternatif (111) sur le côté de l'entraînement hydraulique (120, 121),
    caractérisé par au moins un dispositif de mesure (160, 161, 162), qui permet de déterminer une position du piston hydraulique (111) et/ou d'un angle de rotation (ϕ) d'un arbre (121) destiné au déplacement du piston hydraulique (120) et une position du piston alternatif (x) et/ou une pression (p) dans le premier volume (141),
    le compresseur à piston (100) étant conçu pour introduire, si nécessaire, du fluide hydraulique (a) dans le premier volume (141) et/ou pour l'évacuer du premier volume (141), en fonction de la position du piston hydraulique (120) et/ou de l'angle de rotation (ϕ) de l'arbre (121) destiné au déplacement du piston hydraulique (120) en relation avec la position (x) du piston alternatif (111) et/ou la pression (p) dans le premier volume (141).
  7. Compresseur à piston (100) selon la revendication 6, présentant en outre une unité d'amortissement hydraulique (140) au moyen de laquelle un déplacement du piston alternatif (111) du côté de l'entraînement hydraulique (120, 121) peut si nécessaire être limité à l'aide du fluide hydraulique (a) et par formation d'un deuxième volume (142), qui est limité au moins partiellement par le piston alternatif (111).
  8. Compresseur à piston (100) selon la revendication 7, présentant une première soupape (150), au moyen de laquelle le deuxième volume (142) peut être relié au premier volume (141) et une deuxième soupape (155), au moyen de laquelle du fluide hydraulique (a) peut être évacué à partir du premier volume (141) dans un réservoir (130) pour le fluide hydraulique et/ou
    présentant une troisième soupape (153), au moyen de laquelle le premier volume (141) peut être relié au réservoir (130) pour le fluide hydraulique.
  9. Compresseur à piston (100) selon l'une quelconque des revendications 6 à 8, qui est conçu comme compresseur à piston à plusieurs étages présentant au moins deux pistons alternatifs et des cylindres correspondants.
  10. Compresseur à piston (100) selon l'une quelconque des revendications 6 à 8, dans lequel un liquide ionique est utilisé comme liquide de fonctionnement.
EP18803317.9A 2017-11-22 2018-11-06 Procédé de fonctionnement d' un compresseur à piston et compresseur à piston Active EP3714162B1 (fr)

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DE102017010789.0A DE102017010789A1 (de) 2017-11-22 2017-11-22 Verfahren zum Betreiben eines Kolbenverdichters und Kolbenverdichter
PCT/EP2018/025281 WO2019101361A1 (fr) 2017-11-22 2018-11-06 Procédé pour faire fonctionner un compresseur à piston et compresseur à piston

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JP (1) JP7198818B2 (fr)
KR (1) KR102602056B1 (fr)
CN (1) CN111512044B (fr)
DE (1) DE102017010789A1 (fr)
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CN113107812B (zh) * 2021-04-30 2022-08-30 重庆市南川区金鑫纸业有限公司 造纸用真空系统脱水装置
CN115681073B (zh) * 2022-10-14 2023-11-14 西安交通大学 一种t型楔式离子液体压缩机及其液驱控制方式

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JP3787397B2 (ja) * 1996-11-11 2006-06-21 株式会社三共製作所 流体圧回路の圧損補償装置およびこれを備えたカム装置
AT3213U1 (de) * 1998-03-11 1999-11-25 Hoerbiger Ventilwerke Gmbh Schadraumeinstellungs-einrichtung für kolbenverdichter
JP2006170097A (ja) * 2004-12-16 2006-06-29 Toyota Motor Corp 燃料ポンプ
DE102007033601B3 (de) * 2007-07-17 2008-11-13 Compart Compressor Technology Gmbh & Co. Kg Vorrichtung zur stufenlosen Regulierung des Schadraumvolumens eines Kolbenverdichters
DE102010053091A1 (de) * 2010-12-01 2012-06-06 Linde Aktiengesellschaft Mehrstufiger Kolbenverdichter
DE102011105824B3 (de) * 2011-05-27 2012-05-31 Fresenius Medical Care Deutschland Gmbh Verfahren zur Bestimmung von Gas in einer durch eine Pumpvorrichtung gepumpten Flüssigkeit
FR3020840B1 (fr) * 2014-05-12 2017-03-03 Vianney Rabhi Detendeur de fin de course pour convertisseur de pression a pistons
JP6362008B2 (ja) * 2015-02-09 2018-07-25 Smc株式会社 ポンプシステム及びポンプの異常検出方法
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

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

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