EP3472467B1 - Method and device for compensating pulsation of a compressor - Google Patents

Method and device for compensating pulsation of a compressor Download PDF

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Publication number
EP3472467B1
EP3472467B1 EP17728204.3A EP17728204A EP3472467B1 EP 3472467 B1 EP3472467 B1 EP 3472467B1 EP 17728204 A EP17728204 A EP 17728204A EP 3472467 B1 EP3472467 B1 EP 3472467B1
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EP
European Patent Office
Prior art keywords
piston compressor
torque
phase motor
compressor
crankshaft
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EP17728204.3A
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German (de)
French (fr)
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EP3472467A1 (en
Inventor
Thomas Merkel
Michael Hartl
Stefan Schneider
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Knorr Bremse Systeme fuer Schienenfahrzeuge GmbH
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Knorr Bremse Systeme fuer Schienenfahrzeuge 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
    • 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
    • F04B39/0027—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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/06—Control using electricity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/20—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 changing the driving speed
    • 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
    • F04B53/001—Noise damping
    • 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
    • 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
    • F04B2201/12—Parameters of driving or driven means
    • F04B2201/1202—Torque on the axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2203/00—Motor parameters
    • F04B2203/02—Motor parameters of rotating electric motors
    • F04B2203/0207—Torque

Definitions

  • the invention relates to a method and a device for vibration compensation in a piston compressor, the piston compressor of which is driven by means of a crankshaft from a three-phase motor or the like controlled by a frequency converter. Furthermore, the invention also relates to a piston compressor which is equipped with such a device.
  • the field of application of the invention extends primarily to vehicles, in particular rail vehicles. Since the installation space in vehicles is limited in principle, very compact piston compressors are usually used for this purpose, on which an electric motor is flanged directly, usually multi-stage piston compressors, in order to drive the piston compressor.
  • the load torque M L of a piston compressor in combination with the torque M M of a driving motor, generates an exciter torque about the axis of rotation of the entire piston compressor, which leads to undesirable torsional vibrations. Since, in the case of piston compressors of the type of interest here, the torque M M of the motor follows the load torque M L of the piston compressor with a time delay, the excitation torque increases unfavorably.
  • EP 1 242 741 A1 describes the problem of vibration excitation of piston compressors by load torque M L and motor torque M M and measures to reduce vibrations, which are part of the types of two-stage piston compressors lead to reduced vibration excitation.
  • flywheel masses were used between the engine and the piston compressor, which counteract the excitation of vibrations.
  • this technical solution requires a corresponding amount of material and generates an associated increase in weight.
  • the EP 3 098 448 A1 discloses a method for controlling an electric drive of an electrically driven air compressor. With this method, the load torque is estimated based on an operating parameter in order to reduce the control error on the control loop caused by the load torque.
  • the EP 1 858 153 A2 discloses a method for controlling an electric drive.
  • the system driven by the drive is to be protected against torsional vibrations of the drive.
  • impermissible torsional vibrations are detected via a monitoring device and a control intervention is accordingly carried out via a control device.
  • a motor control method is known to avoid speed changes. For this purpose, an output voltage value or a command value of an inverter is detected and controlled so that the output voltage value or the command value does not exceed a predetermined value.
  • piston compressors are usually operated with three-phase motors, which are assigned a frequency converter.
  • the piston compressor can be controlled with variable speed, in particular to ensure a needs-based To realize compressed air generation within the framework of a corresponding regulation, taking into account minimum switch-on times, intermittent operation intervals and the like.
  • the object is achieved based on a method according to the preamble of claim 1 in conjunction with its characterizing features.
  • the object according to claim 7 is achieved in terms of installation technology.
  • the dependent claims refer back to advantageous developments of the invention.
  • the invention includes the procedural teaching that the current position of the crankshaft of the piston compressor is first determined for vibration compensation, and based on this, a torque M M is specified for the driving three-phase motor by a frequency converter that the Load torque M L of the piston compressor follows, that is, corresponds to this, in order to reduce the vibration excitation of the entire piston compressor. Since the oscillation excitation of the piston compressor arises from the difference between the torque M M of the driving motor and the load moment M L , the oscillation excitation resulting therefrom can be eliminated by a control based on the solution according to the invention. Flywheel masses between the motor and the piston compressor can be reduced or they can be dispensed with entirely.
  • a three-phase motor used within the scope of the solution according to the invention is preferably understood to be a three-phase asynchronous motor or a synchronous reluctance motor.
  • Torque M M specified for the three-phase motor preferably corresponds to the course of the load torque, including a phase length.
  • the torque M M specified for the three-phase motor corresponds to the first order of the load torque curve.
  • a vibration compensation method that is quite easy to implement but very effective consists in simulating only the first-order component in the engine torque M M . Higher orders are neglected.
  • the basis for this is the elastic bearing of the piston compressor. This bearing is designed in such a way that excitations above a certain frequency are kept away from the adjacent structures. This has proved to be sufficient under the circumstances. Higher orders are largely kept away from the elastic bearings. For this reason it is sufficient to eliminate vibration excitations up to and including the first order with the method according to the invention.
  • the deviation of the load torque M L of the piston compressor following the torque M M for the three-phase motor is set in such a way that it is less than 30%.
  • the torque M M of the three-phase motor only approximately follows the load moment M L of the piston compressor, which nevertheless results in effective vibration compensation.
  • the entire vibration behavior can be improved by up to 70% by the electronic compensation according to the invention, with the vibration paths of the piston compressor being significantly reduced, particularly at low speeds.
  • the torque M M generated by the three-phase motor is generated by varying the supply voltage and/or varying the pulse width in the converter.
  • an increase in the torque M M can be achieved by briefly increasing the pulse width.
  • the pulsating load torques usually generated by the piston compressor are smoothed out within the compressor, so that the resulting vibration excitation is further minimized.
  • torque compensation is achieved by counter-regulating the motor current.
  • the torque peak can be compensated for by controlling the IGBT pulse width accordingly and thus by changing the motor current at that moment.
  • a correspondingly fast control and stable intermediate circuit voltage are required for this so-called «space vectoring modulation».
  • the torque M M for the three-phase motor can be increased in a simple manner by the frequency converter by a corresponding increase in the operating voltage.
  • a control unit provided for carrying out the method for vibration compensation according to the invention can advantageously also be integrated directly in the frequency converter.
  • the frequency converter itself is preferably arranged directly on the three-phase motor in order to ensure easy connection to the three-phase source.
  • this electronic assembly can also have at least one sensor input, to connect a position sensor arranged in the area of the motor shaft or the crankshaft to measure the current angular position.
  • the torque requirement to be readjusted depending on the speed is preferably stored in the logic of the control unit implemented in the frequency converter.
  • the piston compressor 1 shows a piston compressor consisting essentially of a piston compressor 1 and a three-phase motor 2 .
  • the piston compressor 1 is designed as a two-stage compressor unit and has two low-pressure cylinders 3a, 3b and a high-pressure cylinder 4 here. Coming from the atmosphere, the compressed air is first precompressed in the low-pressure cylinder 3a, 3b and then brought to an even higher pressure level by the high-pressure cylinder 4 before the compressed air produced is fed to the vehicle for further use.
  • the piston compressor 1 has a crankshaft 5, which is driven by the three-phase motor 2, for actuating the piston drive of the pistons—not shown in more detail—of the cylinders 3a, 3b and 4.
  • the electric three-phase motor 2 is equipped with a frequency converter 6, via which the connection to a three-phase network 7 takes place.
  • the frequency converter 6 is assigned an electronic control unit 8 which is structurally integrated therein.
  • the electronic control unit 8 receives the measurement signal from a position sensor 9 which is arranged in the area of the crankshaft 5 and which specifies the current angular position of the crankshaft 5 for the electronic control unit 8 .
  • FIG. 2 shows a graphic representation of the torque curve in relation to an entire revolution of 0 to 360° of the crankshaft of a piston compressor of the prior art.
  • the average torque of the drive is around 50 Nm (dotted line).
  • the curve of the load torque M L shown is characteristic of two-stage piston compressors, as in figure 1 illustrated. The engine only reacts to the dominating pressure peak with a time delay and, as can be seen, builds up the engine torque M M only out of phase at an angular position of the crankshaft of around 0°.
  • the maximum engine torque MM of approximately 75 Nm only comes into effect when the load torque ML of the piston compressor has already collapsed, here it has even reached its minimum. Due to this effect, three-phase motors even increase due to the design, the torsional vibration excitation in interaction with the piston compressors driven by it.
  • the dominant pressure peak of the load torque M L of around 150 Nm results from the compression of the second stage, namely the high-pressure cylinder.
  • the three-phase drive reacts to this pressure peak and builds up its torque M M of the curve shown.
  • the area between the load moment M L and the torque M M of the engine is marked here as hatched and represents a measure of the vibration excitation around the crankshaft of the piston compressor. Due to the relatively large area of the hatched area, a relatively high disadvantageous vibration excitation can be assumed.
  • FIG 3 shows the torque curve of the torque M M of the motor and the load moment M L of the piston compressor for a full revolution of the crankshaft as a result of the vibration compensation according to the invention.
  • the motor is controlled in such a way that its torque M M corresponds to the load moment M L of the piston compressor follows. It follows from this that the content of the area between the load torque M L and the engine torque M M is minimal compared to the embodiment of the prior art explained above, so that very little vibration excitation takes place.
  • the driving motor builds up its torque M M synchronously and in this respect in a demand-controlled manner with respect to the load torque M L of the piston compressor to be mastered. Due to only minimal irregularities, there is an equally minimal vibration excitation.
  • figure 5 shows the course of the phase currents over time with regard to the three phases of the three-phase motor, which here also turns out to be a fairly uniform respective sine curve due to the almost complete control-technical vibration compensation.
  • the torque curve of the torque M M and the load torque M L for a full revolution of the Crankshaft in contrast to the embodiment described above, here only a compensation with regard to the first order of the load torque curve of the piston compressor is carried out by the torque M M of the three-phase motor.
  • a significantly smaller and evenly distributed surface area between the curves of the engine torque M M of the variable-speed motor and the load torque M L of the piston compressor contributes as a tightened area to excitation of vibrations.
  • the vibration compensation achieved in this way can be regarded as sufficient for the application that is the subject of the invention.

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

Description

Die Erfindung betrifft ein Verfahren sowie eine Einrichtung zur Schwingungskompensation bei einem Kolbenkompressor, dessen Kolbenverdichter mittels Kurbelwelle von einem per Frequenzumrichter angesteuerten Drehstrommotor oder dergleichen angetrieben wird. Ferner betrifft die Erfindung auch einen Kolbenkompressor, der mit einer solchen Einrichtung ausgestattet ist.The invention relates to a method and a device for vibration compensation in a piston compressor, the piston compressor of which is driven by means of a crankshaft from a three-phase motor or the like controlled by a frequency converter. Furthermore, the invention also relates to a piston compressor which is equipped with such a device.

Das Einsatzgebiet der Erfindung erstreckt sicht vornehmlich auf Fahrzeuge, insbesondere Schienenfahrzeuge. Da prinzipiell der Bauraum in Fahrzeugen begrenzt ist, kommen hierfür meist recht kompaktbauende Kolbenkompressoren zum Einsatz, an der meist mehrstufige Kolbenverdichter ein Elektromotor direkt angeflanscht ist, um den Kolbenverdichter anzutreiben. Das Lastmoment ML eines Kolbenverdichters erzeugt im Zusammenspiel mit dem Drehmoment MM eines antreibenden Motors ein Erregermoment um die Drehachse des gesamten Kolbenkompressors, welches zu unerwünschten Drehschwingungen führt. Da bei den Kolbenkompressoren der hier interessierenden Art das Drehmoment MM des Motors dem Lastmoment ML des Kolbenverdichtes zeitverzögert folgt, erhöht sich ungünstiger Weise das Erregermoment.The field of application of the invention extends primarily to vehicles, in particular rail vehicles. Since the installation space in vehicles is limited in principle, very compact piston compressors are usually used for this purpose, on which an electric motor is flanged directly, usually multi-stage piston compressors, in order to drive the piston compressor. The load torque M L of a piston compressor, in combination with the torque M M of a driving motor, generates an exciter torque about the axis of rotation of the entire piston compressor, which leads to undesirable torsional vibrations. Since, in the case of piston compressors of the type of interest here, the torque M M of the motor follows the load torque M L of the piston compressor with a time delay, the excitation torque increases unfavorably.

Aus der DE 100 58 923 A1 geht ein gattungsgemäßer Kolbenkompressor hervor, dessen mehrstufiger Kolbenverdichter mit einem direkt hieran angeflanschten Elektromotor angetrieben wird. Der Kolbenkompressor ist über mehrere schwingungsdämpfende Drahtseilfedern stehend an der Chassis des Fahrzeuges befestigt, um eine Schwingübertragung vom Kolbenkompressor zum Fahrzeug hin zu vermindern.From the DE 100 58 923 A1 a generic piston compressor emerges, the multi-stage piston compressor of which is driven by an electric motor flanged directly to it. The piston compressor is attached to the chassis of the vehicle by means of several vibration-damping wire rope springs in order to reduce the transmission of vibrations from the piston compressor to the vehicle.

Auch die EP 1 242 741 A1 beschreibt die Problematik der Schwingungsanregung von Kolbenkompressoren durch Lastmoment ML und Motormoment MM und Maßnahmen zur Schwingungsreduzierung, die zu Bauarten von zweistufigen Kolbenkompessoren mit reduzierter Schwingungserregung führen. Um den Motoreinfluss auf die Schwinungungserregung zu minimieren, wurden zwischen Motor und Kolbenverdichter Schwungmassen verwendet, welche der Schwingungserregung entgegenwirken. Allerdings verursacht diese technische Lösung einen entsprechenden Materialaufwand und erzeugt eine hiermit verbundene Gewichtssteigerung.Also the EP 1 242 741 A1 describes the problem of vibration excitation of piston compressors by load torque M L and motor torque M M and measures to reduce vibrations, which are part of the types of two-stage piston compressors lead to reduced vibration excitation. In order to minimize the influence of the engine on the excitation of vibrations, flywheel masses were used between the engine and the piston compressor, which counteract the excitation of vibrations. However, this technical solution requires a corresponding amount of material and generates an associated increase in weight.

Die EP 3 098 448 A1 offenbart ein Verfahren zur Regelung eines elektrischen Antriebs eines elektrisch angetriebenen Druckluftverdichters. Bei diesem Verfahren wird das Lastdrehmoment anhand von einem Betriebsparamenter geschätzt, um den durch das Lastdrehmoment verursachten Regelfehler auf den Regelkreis zu reduzieren.the EP 3 098 448 A1 discloses a method for controlling an electric drive of an electrically driven air compressor. With this method, the load torque is estimated based on an operating parameter in order to reduce the control error on the control loop caused by the load torque.

Aus der DE 100 58 924 A1 ist ein mehrstufiger Kolbenkompressor bekannt. Um eine Schwingungsreduktion des Kolbenkompressor zu erzielen, werden an jeder Kröpfung der Kurbelwelle zwei Pleuel angeordnet denen gegenüberliegende Kolben zugeordnet sind.From the DE 100 58 924 A1 a multi-stage piston compressor is known. In order to achieve a vibration reduction of the piston compressor, two connecting rods are arranged on each offset of the crankshaft, to which opposite pistons are assigned.

Die EP 1 858 153 A2 offenbart ein Verfahren zum Steuern eines elektrischen Antriebs. Bei diesem Verfahren soll das vom Antrieb angetriebene System vor Drehschwingungen des Antriebs geschützt werden. Dazu werden über eine Überwachungeinrichtung unzulässige Drehschwingungen detektiert und dementsprechend ein Regeleingriff über eine Regelungseinrichtung durchgeführt.the EP 1 858 153 A2 discloses a method for controlling an electric drive. With this method, the system driven by the drive is to be protected against torsional vibrations of the drive. For this purpose, impermissible torsional vibrations are detected via a monitoring device and a control intervention is accordingly carried out via a control device.

Aus der US 2006/125437 A1 ist ein Motorsteuerungsverfahren bekannt, um Drehzahländerungen zu vermeiden. Dazu wird ein Ausgangsspannungswert oder ein Befehlswerts eines Wechselrichters erfasst und gesteuert, so dass der Ausgangsspannungswert oder der Befehlswert einen Jorbestimmten Wert nicht überschreitet.From the U.S. 2006/125437 A1 a motor control method is known to avoid speed changes. For this purpose, an output voltage value or a command value of an inverter is detected and controlled so that the output voltage value or the command value does not exceed a predetermined value.

In der Praxis werden Kolbenverdichter meist mit Drehstrommotoren betrieben, welchen ein Frequenzumrichter zugeordnet ist. Mit Hilfe des Frequenzumrichters lässt sich der Kolbenverdichter drehzahlvariabel ansteuern, um insbesondere eine bedarfsgerechte Drucklufterzeugung im Rahmen einer entsprechenden Regelung mit Berücksichtigung von Mindesteinschaltzeiten, Aussetzbetriebintervallen und dergleichen zu realisieren.In practice, piston compressors are usually operated with three-phase motors, which are assigned a frequency converter. With the help of the frequency converter, the piston compressor can be controlled with variable speed, in particular to ensure a needs-based To realize compressed air generation within the framework of a corresponding regulation, taking into account minimum switch-on times, intermittent operation intervals and the like.

Bislang waren Frequenzumrichter, insbesondere solche, die für den Schienenfahrzeugbetrieb ausgelegt wurden, recht aufwendig konstruiert und vor allem recht großbauend. Außerdem versorgen diese sogenannten Hilfsbetriebeumrichter auf Schienenfahrzeugen nicht nur einen einzigen elektrischen Verbraucher, sondern mehrere, wie beispielsweise auch Klimaanlagen, Traktionslüfter, Gerätelüfter, Kompressoren und dergleichen. Deshalb konnte bislang ein solcher gebräuchlicher Hilfsbetriebeumrichter nicht auf einen einzelnen Verbraucher abgestimmt werden.So far, frequency converters, especially those designed for rail vehicle operation, have had a very complex design and, above all, have been quite large. In addition, these so-called auxiliary converters on rail vehicles not only supply a single electrical consumer, but several, such as air conditioning systems, traction fans, device fans, compressors and the like. For this reason, such a conventional auxiliary converter could not previously be tuned to an individual consumer.

Durch Weiterentwicklungen der Umrichtertechnik und eine hohe Verfügbarkeit von hierin zum Einsatz kommenden Leistungselektronikbauteilen liegen aktuell Randbedingungen vor, welche es ermöglichen, Frequenzumrichter direkt einem Antrieb zuzuordnen und diese dort auch zu platzieren.Due to further developments in converter technology and a high availability of power electronic components used here, there are currently boundary conditions that make it possible to assign frequency converters directly to a drive and also to place them there.

Es ist daher die Aufgabe der vorliegenden Erfindung ein Verfahren sowie eine Einrichtung zur Schwingungskompensation bei einem Kolbenkompressor zu schaffen, das/die mit einfachen technischen Mitteln eine wirksame Schwingungsunterdrückung in jeder Betriebssituation des Kolbenkompressors ermöglicht.It is therefore the object of the present invention to create a method and a device for compensating for vibrations in a piston compressor, which enables effective vibration suppression in every operating situation of the piston compressor using simple technical means.

Die Aufgabe wird ausgehend von einem Verfahren gemäß dem Oberbegriff von Anspruch 1 in Verbindung mit dessen kennzeichnenden Merkmalen gelöst. Einrichtungstechnisch wird die Aufgabe nach Anspruch 7 gelöst. Die jeweils rückbezogenen abhängigen Ansprüche geben vorteilhafte Weiterbildungen der Erfindung wieder.The object is achieved based on a method according to the preamble of claim 1 in conjunction with its characterizing features. The object according to claim 7 is achieved in terms of installation technology. The dependent claims refer back to advantageous developments of the invention.

Die Erfindung schließt die verfahrenstechnische Lehre ein, dass zur Schwingungskompensation zunächst die aktuelle Position der Kurbelwelle des Kolbenverdichters ermittelt wird, und durch einen Frequenzumrichter hierauf basierend ein Drehmoment MM den antreibenden Drehstrommotor vorgegeben wird, dass dem Lastmoment ML des Kolbenverdichters folgt, diesem also entspricht, um die Schwingungsanregung des gesamten Kolbenkompressors zu reduzieren. Da die Schwingungsanregung des Kolbenkompressors aus der Differenz zwischen Drehmoment MM des antreibenden Motors und Lastmoment ML entsteht, kann durch eine auf der erfindungsgemäßen Lösung basierende Regelung die hieraus resultierende Schwingungsanregung eliminiert werden. Schwungmassen zwischen Motor und Kolbenverdichter können verkleinert werden oder es kann gänzlich hierauf verzichtet werden.The invention includes the procedural teaching that the current position of the crankshaft of the piston compressor is first determined for vibration compensation, and based on this, a torque M M is specified for the driving three-phase motor by a frequency converter that the Load torque M L of the piston compressor follows, that is, corresponds to this, in order to reduce the vibration excitation of the entire piston compressor. Since the oscillation excitation of the piston compressor arises from the difference between the torque M M of the driving motor and the load moment M L , the oscillation excitation resulting therefrom can be eliminated by a control based on the solution according to the invention. Flywheel masses between the motor and the piston compressor can be reduced or they can be dispensed with entirely.

Unter einem im Rahmen der erfindungsgemäßen Lösung zum Einsatz kommenden Drehstrommotor wird vorzugsweise ein Drehstromasynchronmotor oder ein Synchronreluktanzmotor verstanden. Vorzugsweise entspricht das dem Drehstrommotor vorgegebene Drehmoment MM dem Lastmomentenverlauf inklusive einer Phasenlänge. Wobei das dem Drehstrommotor vorgegebene Drehmoment MM der ersten Ordnung des Lastmomentenverlaufs entspricht. Versuche haben ergeben, dass eine recht einfach umzusetzende aber sehr wirksame Schwingungskompensationsmethode darin besteht, eben nur den Anteil der ersten Ordnung im Motormoment MM nachzubilden. Höhere Ordnungen werden dabei vernachlässigt. Grundlage hierfür stellt die elastische Lagerung des Kolbenkompressors dar. Diese Lagerung ist so ausgelegt, dass Anregungen oberhalb einer bestimmten Frequenz von Anschlusskonstruktionen ferngehalten werden. Dies hat sich unter diesen Umständen als hinreichend erwiesen. Höhere Ordnungen werden von den elastischen Lagerungen weitgehend ferngehalten. Aus diesem Grunde ist es ausreichend, Schwingungsanregungen bis einschließlich der ersten Ordnung mit dem erfindungsgemäßen Verfahren zu eliminieren.A three-phase motor used within the scope of the solution according to the invention is preferably understood to be a three-phase asynchronous motor or a synchronous reluctance motor. Torque M M specified for the three-phase motor preferably corresponds to the course of the load torque, including a phase length. The torque M M specified for the three-phase motor corresponds to the first order of the load torque curve. Experiments have shown that a vibration compensation method that is quite easy to implement but very effective consists in simulating only the first-order component in the engine torque M M . Higher orders are neglected. The basis for this is the elastic bearing of the piston compressor. This bearing is designed in such a way that excitations above a certain frequency are kept away from the adjacent structures. This has proved to be sufficient under the circumstances. Higher orders are largely kept away from the elastic bearings. For this reason it is sufficient to eliminate vibration excitations up to and including the first order with the method according to the invention.

Ebenso hinreichend ist es wenn die Abweichung des dem Drehmoment MM für den Drehstrommotor folgende Lastmoment ML des Kolbenverdichters derart eingestellt ist, dass dieses kleiner als 30% ist. Im Rahmen dieses Abweichungsbereichs folgt das Drehmoment MM des Drehstrommotors nur annähernd dem Lastmoment ML des Kolbenverdichters, was dennoch eine wirksame Schwingungskompensation ergibt. Im Rahmen aller konstruktiver Randbedingungen hat sich gezeigt, dass das gesamte Schwingungsverhalten durch die erfindungsgemäße elektronische Kompensation um bis zu 70% verbessert werden kann, wobei die Schwingwege des Kolbenkompressors insbesondere bei kleinen Drehzahlen deutlich reduziert werden.It is also sufficient if the deviation of the load torque M L of the piston compressor following the torque M M for the three-phase motor is set in such a way that it is less than 30%. Within this deviation range, the torque M M of the three-phase motor only approximately follows the load moment M L of the piston compressor, which nevertheless results in effective vibration compensation. Within the framework of all structural boundary conditions, it has been shown that the entire vibration behavior can be improved by up to 70% by the electronic compensation according to the invention, with the vibration paths of the piston compressor being significantly reduced, particularly at low speeds.

Gemäß einer weiteren die Erfindung verbessernden Maßnahme wird vorgeschlagen, dass zur Kompensation von Drehzahlschwankungen das vom Drehstrommotor generierte Drehmoment MM durch eine Variation der Speisespannung und/oder eine Variation der Pulsbreite im Umrichter erzeugt wird. Somit kann beispielsweise eine Erhöhung des Drehmoments MM erreicht werden, indem die Pulsbreite kurzzeitig vergrößert wird. Hierdurch werden die gewöhnlich vom Kolbenverdichter erzeugten pulsierenden Lastmomente innerhalb des Kompressors geglättet, so dass die hiervon ausgehende Schwingungsanregung weiter minimiert wird. Da das Drehmoment MM des Drehstrommotors proportional zum Motorstrom ist, wird eine Momentenkompensation durch eine Gegenregelung des Motorstroms erreicht. Die Drehmomentspitze kann durch eine entsprechende Ansteuerung der IGBT-Pulsbreite und somit durch einen in diesem Moment veränderten Motorstrom kompensiert werden. Eine entsprechend schnelle Steuerung und stabile Zwischenkreisspannung sind für diese sogenannte «Space Vectoring Modulation» erforderlich.According to a further measure improving the invention, it is proposed that, to compensate for speed fluctuations, the torque M M generated by the three-phase motor is generated by varying the supply voltage and/or varying the pulse width in the converter. Thus, for example, an increase in the torque M M can be achieved by briefly increasing the pulse width. As a result, the pulsating load torques usually generated by the piston compressor are smoothed out within the compressor, so that the resulting vibration excitation is further minimized. Since the torque M M of the three-phase motor is proportional to the motor current, torque compensation is achieved by counter-regulating the motor current. The torque peak can be compensated for by controlling the IGBT pulse width accordingly and thus by changing the motor current at that moment. A correspondingly fast control and stable intermediate circuit voltage are required for this so-called «space vectoring modulation».

Vorzugsweise kann eine Erhöhung des Drehmoments MM für den Drehstrommotor durch eine entsprechende Erhöhung der Betriebsspannung in einfacher Weise vom Frequenzumrichter durchgeführt werden. Eine zur Durchführung des erfindungsgemäßen Verfahrens zur Schwingungskompensation vorgesehene Steuereinheit kann vorteilhafterweise direkt im Frequenzumrichter mit integriert werden. Der Frequenzumrichter selbst ist vorzugsweise direkt am Drehstrommotor angeordnet, um einen einfachen Anschluss an die Drehstromquelle zu gewährleisten. Außerdem kann diese elektronische Baueinheit auch mindestens einen Sensoreingang aufweisen, um hieran einen im Bereich der Motorwelle oder der Kurbelwelle angeordneten Positionssensor zur Messung der aktuellen Winkelstellung anzuschließen. Vorzugsweise ist der je nach Drehzahl nachzuregelnde Drehmomentenbedarf in der Logik der im Frequenzumrichter implementierten Steuereinheit hinterlegt.Preferably, the torque M M for the three-phase motor can be increased in a simple manner by the frequency converter by a corresponding increase in the operating voltage. A control unit provided for carrying out the method for vibration compensation according to the invention can advantageously also be integrated directly in the frequency converter. The frequency converter itself is preferably arranged directly on the three-phase motor in order to ensure easy connection to the three-phase source. In addition, this electronic assembly can also have at least one sensor input, to connect a position sensor arranged in the area of the motor shaft or the crankshaft to measure the current angular position. The torque requirement to be readjusted depending on the speed is preferably stored in the logic of the control unit implemented in the frequency converter.

Weitere die Erfindung verbessernde Maßnahmen werden nachstehend gemeinsam mit der Beschreibung eines bevorzugten Ausführungsbeispiels der Erfindung anhand der Figuren näher dargestellt. Es zeigt

Fig. 1
eine Blockschaltbilddarstellung eines Kolbenkompressors mit hierin integrierter Einrichtung zur Schwingungskompensation,
Fig. 2
eine graphische Darstellung der von Motor und Verdichter erzeugten Drehschwingungen gemäß des Standes der Technik,
Fig. 3
eine graphische Darstellung der von Motor und Verdichter erzeugten Drehschwingungen gemäß der erfindungsgemäßen Lösung hinsichtlich einer ersten Ausführungsform, und
Fig. 4
eine graphische Darstellung des Drehzahlverlaufs bei der ersten Ausführungsform,
Fig. 5
eine graphische Darstellung des zeitlichen Verlaufs der Strangströme eines Drehstrommotors als Antrieb gemäß der ersten Ausführungsform,
Fig. 6
eine graphische Darstellung der von Motor und Verdichter erzeugten Drehschwingungen gemäß der erfindungsgemäßen Lösung hinsichtlich einer zweiten Ausführungsform
Fig. 7
eine graphische Darstellung des Drehzahlverlaufs bei der zweiten Ausführungsform,
Fig. 8
eine graphische Darstellung des zeitlichen Verlaufs der Strangströme eines Drehstrommotors als Antrieb gemäß der zweiten Ausführungsform.
Further measures improving the invention are presented in more detail below together with the description of a preferred exemplary embodiment of the invention with reference to the figures. It shows
1
a block diagram representation of a piston compressor with an integrated device for vibration compensation,
2
a graphical representation of the torsional vibrations generated by the engine and compressor according to the prior art,
3
a graphical representation of the torsional vibrations generated by the engine and compressor according to the solution according to the invention with regard to a first embodiment, and
4
a graphical representation of the speed curve in the first embodiment,
figure 5
a graphic representation of the time course of the phase currents of a three-phase motor as a drive according to the first embodiment,
6
a graphical representation of the torsional vibrations generated by the engine and compressor according to the solution according to the invention with regard to a second embodiment
7
a graphical representation of the speed curve in the second embodiment,
8
a graphical representation of the time course of the phase currents of a three-phase motor as a drive according to the second embodiment.

Fig. 1 zeigt einen im Wesentlichen aus Kolbenverdichter 1 und Drehstrommotor 2 bestehenden Kolbenkompressor. Der Kolbenverdichter 1 ist als eine zweistufige Verdichtereinheit ausgebildet und weist hier zwei Niederdruckzylinder 3a, 3b sowie einen Hochdruckzylinder 4 auf. Die Druckluft wird von der Atmosphäre kommend zunächst im Niederdruckzylinder 3a, 3b vorkomprimiert und anschließend vom Hochdruckzylinder 4 auf ein noch höheres Druckniveau gebracht, ehe diese erzeugte Druckluft der weiteren Verwertung im Fahrzeug zugeführt wird. 1 shows a piston compressor consisting essentially of a piston compressor 1 and a three-phase motor 2 . The piston compressor 1 is designed as a two-stage compressor unit and has two low-pressure cylinders 3a, 3b and a high-pressure cylinder 4 here. Coming from the atmosphere, the compressed air is first precompressed in the low-pressure cylinder 3a, 3b and then brought to an even higher pressure level by the high-pressure cylinder 4 before the compressed air produced is fed to the vehicle for further use.

Der Kolbenverdichter 1 weist zur Betätigung des Kolbentriebs von - nicht weiter dargestellten - Kolben der Zylinder 3a, 3b und 4 eine Kurbelwelle 5 auf, welche vom Drehstrommotor 2 angetrieben wird. Der elektrische Drehstrommotor 2 ist mit einem Frequenzumrichter 6 ausgestattet, über welchen der Anschluss an ein Drehstromnetz 7 erfolgt. Dem Frequenzumrichter 6 ist eine elektronische Steuereinheit 8 zugeordnet, welche hierin baulich integriert ist. Eingangsseitig empfängt die elektronsiche Steuereinheit 8 das Messsignal eines im Bereich der Kurbelwelle 5 angeordneten Positionssensors 9, welcher der elektronischen Steuereinheit 8 die aktuelle Winkelstellung der Kurbelwelle 5 vorgibt.The piston compressor 1 has a crankshaft 5, which is driven by the three-phase motor 2, for actuating the piston drive of the pistons—not shown in more detail—of the cylinders 3a, 3b and 4. The electric three-phase motor 2 is equipped with a frequency converter 6, via which the connection to a three-phase network 7 takes place. The frequency converter 6 is assigned an electronic control unit 8 which is structurally integrated therein. On the input side, the electronic control unit 8 receives the measurement signal from a position sensor 9 which is arranged in the area of the crankshaft 5 and which specifies the current angular position of the crankshaft 5 for the electronic control unit 8 .

Fig. 2 zeigt in graphischer Darstellung den Drehmomentenverlauf bezüglich einer gesamten Umdrehung 0 bis 360° der Kurbelwelle eines Kolbenverdichters des Standes der Technik. Das durchschnittliche Drehmoment des Antriebs liegt bei etwa 50 Nm (Punktlinie). Im Verlauf des Lastmoments ML ist zu erkennen, dass dieses aufgrund einer Druckspitze bei circa 200° Winkelstellung der Kurbelwelle ein Maximum von etwa 140 Nm aufweist. Der dargestellte Verlauf des Lastmoments ML ist charakteristisch für zweistufige Kolbenverdichter, wie in Figur 1 illustriert. Der Motor reagiert auf die dominierende Druckspitze erst zeitverzögert und baut ersichtlicherweise das Motormoment MM erst phasenversetzt bei circa 0° Winkelstellung der Kurbelwelle auf. Somit kommt das maximale Motormoment MM von circa 75 Nm erst dann zur Wirkung, wenn das Lastmoment ML des Kolbenverdichters bereits eingebrochen ist, hier sogar sein minimum erreicht hat. Durch diesen Effekt erhöhen Drehstrommotoren sogar bauartbedingt die Drehschwingungsanregung im Zusammenwirken mit den hiervon angetriebenen Kolbenverdichtern. Die dominierende Druckspitze des Lastmomentes ML von circa 150 Nm resultiert aus der Verdichtung der zweiten Stufe, nämlich dem Hochdruckzylinder. Der Drehstromantrieb reagiert auf diese Druckspitze und baut sein Drehmoment MM des dargestellten Verlaufs auf. Die Fläche zwischen dem Lastmoment ML und dem Drehmoment MM des Motors ist hier straffiert gekennzeichnet und stellt ein Maß für die Schwingungsanregung um die Kurbelwelle des Kolbenverdichters dar. Wegen des recht großen Flächeninhaltes der straffierten Fläche ist von einer relativ hohen nachteilhaften Schwingungsanregung auszugehen. 2 shows a graphic representation of the torque curve in relation to an entire revolution of 0 to 360° of the crankshaft of a piston compressor of the prior art. The average torque of the drive is around 50 Nm (dotted line). In the course of the load torque M L it can be seen that this has a maximum of about 140 Nm due to a pressure peak at an angular position of the crankshaft of about 200°. The curve of the load torque M L shown is characteristic of two-stage piston compressors, as in figure 1 illustrated. The engine only reacts to the dominating pressure peak with a time delay and, as can be seen, builds up the engine torque M M only out of phase at an angular position of the crankshaft of around 0°. Thus, the maximum engine torque MM of approximately 75 Nm only comes into effect when the load torque ML of the piston compressor has already collapsed, here it has even reached its minimum. Due to this effect, three-phase motors even increase due to the design, the torsional vibration excitation in interaction with the piston compressors driven by it. The dominant pressure peak of the load torque M L of around 150 Nm results from the compression of the second stage, namely the high-pressure cylinder. The three-phase drive reacts to this pressure peak and builds up its torque M M of the curve shown. The area between the load moment M L and the torque M M of the engine is marked here as hatched and represents a measure of the vibration excitation around the crankshaft of the piston compressor. Due to the relatively large area of the hatched area, a relatively high disadvantageous vibration excitation can be assumed.

Fig. 3 stellt den Drehmomentenverlauf des Drehmoments MM des Motors und des Lastmoments ML des Kolbenverdichtes für eine volle Umdrehung der Kurbelwelle in Folge der erfindungsgemäßen Schwingungskompensation dar. Bei dieser Ausführungsform erfolgt die Ansteuerung des Motors derart, dass dessen Drehmoment MM dem Lastmoment ML des Kolbenverdichters folgt. Hieraus ergibt sich, dass der Flächeninhalt der Fläche zwischen Lastmoment ML und Motormoment MM gegenüber der vorstehend erläuterten Ausführungsform des Standes der Technik minimal ist, so dass eine sehr geringe Schwingungsanregung erfolgt. Denn der antreibende Motor baut aufgrund der erfindungsgemäßen Steuerung sein Drehmoment MM synchron und insoweit bedarfsgesteuert zum zu bewältigenden Lastmoment ML des Kolbenverdichters auf. Aufgrund nur minimaler Ungleichförmigkeiten erfolgt eine ebenso minimale Schwingungsanregung. 3 shows the torque curve of the torque M M of the motor and the load moment M L of the piston compressor for a full revolution of the crankshaft as a result of the vibration compensation according to the invention. In this embodiment, the motor is controlled in such a way that its torque M M corresponds to the load moment M L of the piston compressor follows. It follows from this that the content of the area between the load torque M L and the engine torque M M is minimal compared to the embodiment of the prior art explained above, so that very little vibration excitation takes place. Because of the control according to the invention, the driving motor builds up its torque M M synchronously and in this respect in a demand-controlled manner with respect to the load torque M L of the piston compressor to be mastered. Due to only minimal irregularities, there is an equally minimal vibration excitation.

Fig. 4 illustriert in Konsequenz dessen einen gleichförmigen Verlauf der Drehzahl n der Kurbelwelle über die gesamte Umdrehung. Dieser entspricht auch in etwa dem mittleren Verlauf der Drehzahl n'. 4 consequently illustrates a uniform progression of the rotational speed n of the crankshaft over the entire revolution. This also roughly corresponds to the average course of the speed n'.

Fig. 5 zeigt den zeitlichen Verlauf der Strangströme bezüglich der drei Phasen des Drehstrommotors, welcher hier aufgrund der fast kompletten steuerungstechnischen Schwingungskompensation auch als recht gleichförmige jeweilige Sinuskurve ausfällt. figure 5 shows the course of the phase currents over time with regard to the three phases of the three-phase motor, which here also turns out to be a fairly uniform respective sine curve due to the almost complete control-technical vibration compensation.

Fig. 6 illustriert hinsichtlich der zweiten Ausführungsform den Drehmomentenverlauf des Drehmoments MM sowie des Lastmoments ML für eine volle Umdrehung der Kurbelwelle, wobei im Gegensatz zur vorstehend beschriebenen Ausführungsform hier lediglich eine Kompensation hinsichtlich der ersten Ordnung des Lastmomentenverlaufs des Kolbenverdichters durch das Drehmoment MM des Drehstrommotors erfolgt. Daraus ergibt sich, dass im Vergleich zum vorstehend erläuterten Stand der Technik ein deutlich geringerer und gleichmäßig verteilter Flächeninhalt zwischen den Kurven des Verlaufs des Motormoments MM des Drehzahlmotors und des Lastmoments ML des Kolbenverdichers als straffierte Fläche zu einer Schwingungsanregung beiträgt. Die hierdurch erzielte Schwingungskompensation kann als hinreichend für die erfindungsgegenständliche Anwendung angesehen werden. 6 illustrated with respect to the second embodiment, the torque curve of the torque M M and the load torque M L for a full revolution of the Crankshaft, in contrast to the embodiment described above, here only a compensation with regard to the first order of the load torque curve of the piston compressor is carried out by the torque M M of the three-phase motor. As a result, compared to the prior art explained above, a significantly smaller and evenly distributed surface area between the curves of the engine torque M M of the variable-speed motor and the load torque M L of the piston compressor contributes as a tightened area to excitation of vibrations. The vibration compensation achieved in this way can be regarded as sufficient for the application that is the subject of the invention.

Fig. 7 zeigt in Konsequenz dessen, dass die Drehzahl n der Kurbelwelle nur geringfügig um die mittlere Drehzahl n' schwankt. Eine weitgehende Gleichförmigkeit des Drehzahlverlaufs kann also hier durch die Kompensation der ersten Ordnung des Lastmomentenverlaufs des Kolbenverdichters erzielt werden. 7 consequently shows that the rotational speed n of the crankshaft fluctuates only slightly around the mean rotational speed n′. Extensive uniformity of the speed curve can be achieved here by compensating for the first order of the load torque curve of the piston compressor.

Fig. 8 stellt dementsprechend den zeitlichen Verlauf der Strangströme der drei Phasen des Drehstrommotors dar, welche zwar im Gegensatz zu der vorstehend erörterten quasi vollständigen Erfindungskompensation eine geringfügige Ungleichförmigkeit erkennen lässt. Gleichwohl hält sich der Strangstromverlauf in engen Grenzen, was die Wirkung der erfindungsgemäßen Lösung gemäß der zweiten Ausführungsform belegt. 8 12 accordingly represents the time profile of the phase currents of the three phases of the three-phase motor, which, in contrast to the quasi-complete inventive compensation discussed above, reveals a slight non-uniformity. Nevertheless, the phase current progression is kept within narrow limits, which proves the effect of the solution according to the invention according to the second embodiment.

In einem weiteren Ausführungsbeispiel ist es beispielsweise auch möglich, anstelle eines zweistufigen Kolbenkompressors auch einen einstufigen Kolbenkompressor mit der erfindungsgemäßen steuerungstechnischen Schwingungskompensation auszurüsten.In a further exemplary embodiment, it is also possible, for example, to equip a single-stage piston compressor with the control-technical vibration compensation according to the invention instead of a two-stage piston compressor.

BEZUGSZEICHENLISTEREFERENCE LIST

11
Kolbenverdichterpiston compressor
22
Drehstrommotorthree-phase motor
33
Niederdruckzylinderlow pressure cylinder
44
Hochdruckzylinderhigh pressure cylinder
55
Kurbelwellecrankshaft
66
Frequenznumrichterfrequency converter
77
Drehstromquellethree-phase source
88th
Steuereinheitcontrol unit
99
Positionssensorposition sensor
MLML
Lastmoment KolbenverdichterLoad torque piston compressor
MMmm
Drehmoment DrehstrommotorTorque three-phase motor
nn
Drehzahlrotation speed
n'n'
durchschnittliche Drehzahlaverage speed

Claims (10)

  1. Method for vibration compensation in a reciprocating compressor, the piston compressor (1) of which is driven by means of a crankshaft (5) of a three-phase motor (2) controlled by a frequency converter (6),
    characterised in that the current angular position of the crankshaft (5) of the piston compressor (1) is determined, and, based on this, a torque (MM) that follows the load moment (ML) of the piston compressor (1) is prescribed by the frequency converter (6) for the three-phase motor (2) in order to reduce the vibration excitation of the reciprocating compressor as a whole, wherein the torque (MM) prescribed for the three-phase motor (2) corresponds to the first order of the load moment profile of the piston compressor (1).
  2. Method according to claim 1,
    characterised in that the torque (MM) prescribed for the three-phase motor (2) corresponds to the phase position and the load moment profile of the piston compressor (1).
  3. Method according to claim 1,
    characterised in that the current angular position of the crankshaft (5) of the piston compressor (1) is determined by sensors
  4. Method according to claim 1,
    characterised in that the deviation of the load moment (ML) of the piston compressor (1) following the torque (MM) for the three-phase motor (2) is set in such a way that it is less than 30%.
  5. Method according to claim 1,
    characterised in that an increase of the torque (MM) for the three-phase motor (2) is carried out by a corresponding increase of its operating voltage by the frequency converter (6).
  6. Method according to any of the preceding claims,
    characterised in that, to compensate for fluctuations in speed, the torque (MM) generated by the three-phase motor (2) is produced by the frequency converter (6) by a variation of the feed voltage and/or a variation of the pulse width.
  7. Apparatus for vibration compensation in a reciprocating compressor, the piston compressor (1) of which is driven by means of a crankshaft (5) by a three-phase motor (2) controlled by a frequency converter (6),
    characterised in that the apparatus comprises a control unit (8) integrated into the frequency converter (6), wherein the current angular position of the crankshaft (5) of the piston compressor (1) can be determined by means of the control unit (8), and wherein, based on this, a torque (MM) that corresponds to the load moment (ML) of the piston compressor (1) for the three-phase motor (2) can be prescribed in order to reduce the vibration excitation of the reciprocating compressor as a whole.
  8. Apparatus according to claim 7,
    characterised in that, in the region of the motor shaft or the crankshaft (5), there is arranged a position sensor (9) that measures its current angular position, in order to make the measured value available to the control unit (8).
  9. Apparatus according to claim 7,
    characterised in that the frequency converter (6) is located in or at the three-phase motor (2)
  10. Reciprocating compressor for producing compressed air, in particular for a vehicle, comprising a piston compressor (1), which drives a three-phase motor (2) flange-mounted thereon, and apparatus for vibration compensation according to any of the preceding claims 7 to 9.
EP17728204.3A 2016-06-17 2017-06-07 Method and device for compensating pulsation of a compressor Active EP3472467B1 (en)

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DE102016111101A1 (en) 2017-12-21
WO2017215991A1 (en) 2017-12-21
EP3472467A1 (en) 2019-04-24
CN109477473A (en) 2019-03-15
CN109477473B (en) 2020-08-18
US20190264676A1 (en) 2019-08-29

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