EP0254005A1 - Method for the improvement of the regularity with a piston engine and engine running according to this method - Google Patents

Method for the improvement of the regularity with a piston engine and engine running according to this method Download PDF

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Publication number
EP0254005A1
EP0254005A1 EP87108248A EP87108248A EP0254005A1 EP 0254005 A1 EP0254005 A1 EP 0254005A1 EP 87108248 A EP87108248 A EP 87108248A EP 87108248 A EP87108248 A EP 87108248A EP 0254005 A1 EP0254005 A1 EP 0254005A1
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EP
European Patent Office
Prior art keywords
shaft
torsional vibrations
internal combustion
combustion engine
cylinders
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Granted
Application number
EP87108248A
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German (de)
French (fr)
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EP0254005B1 (en
Inventor
Jean Jenzer
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Sulzer AG
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Sulzer AG
Gebrueder Sulzer AG
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
    • F02B75/18—Multi-cylinder engines
    • F02B75/20—Multi-cylinder engines with cylinders all in one line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/02—Circuit arrangements for generating control signals
    • F02D41/14—Introducing closed-loop corrections
    • F02D41/1497—With detection of the mechanical response of the engine
    • F02D41/1498—With detection of the mechanical response of the engine measuring engine roughness
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
    • F02B75/18—Multi-cylinder engines
    • F02B2075/1804—Number of cylinders
    • F02B2075/1824—Number of cylinders six
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/24—Electrical control of supply of combustible mixture or its constituents characterised by the use of digital means
    • F02D41/26—Electrical control of supply of combustible mixture or its constituents characterised by the use of digital means using computer, e.g. microprocessor
    • F02D41/28—Interface circuits
    • F02D2041/286—Interface circuits comprising means for signal processing
    • F02D2041/288—Interface circuits comprising means for signal processing for performing a transformation into the frequency domain, e.g. Fourier transformation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D2200/00—Input parameters for engine control
    • F02D2200/02—Input parameters for engine control the parameters being related to the engine
    • F02D2200/10—Parameters related to the engine output, e.g. engine torque or engine speed
    • F02D2200/1015—Engines misfires

Definitions

  • the present invention relates to a method for improving the synchronism of a reciprocating piston internal combustion engine with volumetric fuel supply, in the stationary operating state, with three or more cylinders, and a reciprocating piston internal combustion engine for carrying out the method.
  • the control and monitoring of the synchronism of such reciprocating internal combustion engines, such as diesel engines, has hitherto been carried out by monitoring the speed of the output shaft or the shaft of a machine driven by the engine.
  • the regulation itself is carried out by changing the injection quantity of all injection pumps, which are switched on to the individual cylinders in a certain cycle.
  • This known type of regulation takes into account and regulates the constancy of the rotational speed in the sense that with the change in the injection quantity, this is changed in the same way for all cylinders if it is assumed that the injection quantity in each cylinder is the same.
  • the invention provides a remedy here and ensures that the reciprocating piston internal combustion engine has a significantly improved synchronism behavior in this respect.
  • Such a method for improving the same is according to the invention running a three- or multi-cylinder reciprocating internal combustion engine, characterized in that the torsional vibrations of at least one order of the drive shaft are minimized by changing the indicated mean cylinder pressure of at least one cylinder.
  • the invention further relates to a reciprocating piston internal combustion engine for carrying out the method and advantageous special embodiments of the method and the reciprocating piston internal combustion engine.
  • the torsional vibrations or their amplitudes and angular position are measured with the torsional vibration meter 3 measured continuously at the shaft end l23 and fed to the Fourier analyzer 4. In the Fourier analyzer 4, the Fourier decomposition of the torsional vibrations into members of different orders is carried out.
  • the crank star method is a simple approximation method, for example, the torsional vibrations are minimized iteratively, ie in several cycles or steps.
  • correction signals are generated which are fed to the relevant injection pumps 61, 62, 63, 64, 65, 66. Due to the corrections, a new steady state is established in the course of the diesel engine 1. After this is reached the torsional vibrations are measured and analyzed again in a further control cycle and other correction signals are generated on the basis of the analysis results and the torsional vibrations are further minimized.
  • the control cycle advantageously extends over the time of several working cycles (revolutions) of the diesel engine 1. It is thus achieved that the stochastic changes in the indicated cylinder mean pressure from ignition to ignition of the individual cylinders 16l, 1662, 1663, 1664, 1665, 1666 only negligibly affect the torsional vibration signal to be evaluated.
  • torsional vibrations e.g. a device available on the market under the name angle encoder (optical incremental encoder, type G 70 from Litton).
  • An injection pump that is suitable for changing the injection quantity is e.g. described in DE-OS 3l 00 725.2-l3.
  • Fourier analyzers are also known and commercially available (e.g. CAT 25l5 from Genrad).
  • the two-stroke diesel engine l from FIG. 2 with the six cylinders l6l to l66 drives the ship propeller 7 via the shaft 22.
  • the other end of the crankshaft 22 of the diesel engine is connected via a clutch l8 to a transmission gear 8 which drives a hydraulic pump 8l .
  • This pump 8l is part of a hydrostatic transmission, which forms a closed hydraulic pressure medium circuit together with the hydrostatic motor 82.
  • This circuit is supplied with hydrostatic pressure medium, for example oil, through the low-pressure station 83, which contains a pressure medium reservoir, a feed pump, an overflow line with overflow valve, filter, etc.
  • the hydrostatic motor 82 drives the electric generator 9 via a shaft 89.
  • the speed of the shaft 89 and thus of the generator 9 is monitored by the sensor 84, from which the measured actual value is fed to the speed controller 85 and in which the Actual value is compared with the specified target value.
  • the generator 9 delivers the electrical energy to the vehicle electrical system 100.
  • the amount of pressure medium flowing through the hydrostatic motor 82 is changed by the controller signals being fed via the signal line 86 to an actuator in the motor 82.
  • the torsional vibration meter 3 measures the torsional vibrations of the shaft of the generator 9.
  • the determination of the correction signals which are fed to the injection pumps 6l, 62, 63, 64, 65, 66 are carried out in the same way as for the system from FIG. l described, determined.
  • the torsional vibrations generated by the diesel engine 1 are partially transmitted to the engine 82 and the shaft of the generator via the hydrostatic circuit.
  • the shaft l7 of the diesel engine 1 drives the adjustable ship propeller 72 via the coupling 7l and shaft 73.
  • the shaft l7 ⁇ of the diesel engine l drives the generator via a transmission 9l 9, which delivers the electrical current to the vehicle electrical system 100.
  • the torsional vibrations and their amplitudes and Angular positions are measured with the torsional vibration meter 3 on the shaft of the generator 9 and continuously fed to the Fourier analyzer 4.
  • the Fourier decomposition of the torsional vibrations into members of different orders is carried out.
  • the correction signals for the change in the injection quantity of the injection pumps 6l, 62, 63, 64, 65, 66 are in the injection pump controller 5, which includes a computer, for example on the basis of the elements of the first and second order, for example according to the crank star method, which is based on Fig. 3 is explained.
  • the shaft l7 of the diesel engine drives, via the clutch 71, the shaft 73 with the adjustable marine propeller 72.
  • the gear 92 is connected as a secondary gear to the shaft of the diesel engine 1 and drives the generator via a clutch 94 9.
  • the generator 9 supplies electrical energy to the vehicle electrical system 100.
  • the torsional vibrations of the shaft of the generator 9 are continuously determined with the torsional vibration meter 3 according to their amplitude and angular position and fed to the Fourier analyzer 4.
  • the torsional vibrations are broken down into links of different orders in the Fourier analyzer 4.
  • the shaft l7 of the diesel engine 1 drives the shaft 73 with the adjustable ship propeller 72 via the clutch 71.
  • the gear 93 is driven directly by the shaft 73 and in turn drives via the clutch 94, the generator 9.
  • the generator 9 supplies electrical energy to the vehicle electrical system 100.
  • the amplitude and angular position of the torsional vibrations are continuously measured on the shaft of the generator 9 and the Fourier analyzer 4 fed.
  • the Fourier analyzer 4 the Fourier decomposition of the torsional vibrations into members of different orders takes place.
  • the correction signals for the injection pumps 61, 62, 63, 64, 65 and 66 can be determined in the systems of FIGS. 2A, 2B and 2C in the same way as described for FIG. 1.
  • crank star method for determining the correction factors for correcting the injection quantity for minimizing the torsional vibrations of the first order is explained.
  • the simplifying assumptions are made that - The average indicated cylinder pressure of a cylinder does not deviate from the target value by more than 5%.
  • the disturbance amplitude changes linearly with the disturbance and the phase remains the same.
  • the measured disturbance, ie a measured torsional vibration can be minimized by correcting the mean indicated cylinder pressure of two or, in special cases, one cylinder, ie the disturbance is generated by the corresponding cylinder.
  • the firing order of the engine is l, 6, 2, 4, 3, 5.
  • the pole diagram l9 are the calculated torsional vibration vectors l9l to l96, first order of the shaft of a six-cylinder engine for all six cases that one of the cylinders has a 5% reduction in the yields mean indicated cylinder pressure, shown in dashed lines.
  • These vectors l9l to l96 form the so-called first-order correction crank stars.
  • the ends of these vectors l9l to l96 lie on a circle whose center M is not in the zero point P of the pole diagram, but is shifted by a vector l90.
  • This vector l90 corresponds to the torsional vibration vector of the ideal, i.e. fully balanced engine.
  • crank star l9l ⁇ to l96 ⁇ is now used to determine the corrections to the mean indicated cylinder pressure in one or two cylinders.
  • a torsional vibration S (amplitude and phase) is measured on the shaft and the vector is drawn in the shifted correction crank star
  • S lies between two vectors of the shifted correction crank star, in our example between the vectors l9l ⁇ and l96 ⁇ , or falls in the direction of one of the vectors l9l ⁇ to l96 ⁇ .
  • the decomposition of the amplitude vector S into the two vectors S1 and S6 in the direction of the two vectors of the correction crank star is interpreted as a disturbance of the two cylinders 1 and 2. Since the correction crank star is based on the assumption of underperformance of the disturbed cylinders, but the cylinders could also perform too much, this decomposition must be calculated in the correct vector basis.
  • This base is a pair of the vectors Z1, Z6, Z3 and Z4. The correction factor for the two cylinders of a pair combination thus results directly from the correction crank star.
  • each fault can be attributed to two faulty cylinders, for example, usually makes it necessary to iteratively minimize the to carry out in several steps.
  • a single correction factor for only one cylinder is obtained if the vector of the measured disturbance coincides with one of the vectors l9l ⁇ to l96 ⁇ .
  • the described way of minimizing the torsional vibrations has proven to be very favorable in practice.
  • the invention is in no way limited to the exemplary embodiments described, but rather comprises any method for improving the synchronism of reciprocating piston internal combustion engines, in which correction factors acting on the indicated medium pressure are determined in a different way.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Combined Controls Of Internal Combustion Engines (AREA)
  • Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
  • Control Of Vehicle Engines Or Engines For Specific Uses (AREA)

Abstract

1. Method of evening out the steady-state running of a reciprocating internal combustion engine having three or more cylinders, wherein the mean indicated pressure of at least one cylinder is varied, characterised in that at least one order of the torsional vibrations of the drive system is minimized by : in a first step of the method : measuring the torsional vibrations at the drive shaft or at a shaft (12, 22) connected kinematically to the drive shaft, by means of a torsional vibration meter (3), in a second step of the method : subjecting the measured torsional vibrations to a Fourier analysis for torsional vibrations, in a third step of the method : determining correction factors for the variation of the mean indicated cylinder pressure of at least two cylinders in a computer from the ascertained amounts and phase positions of the torsional vibration amplitudes and from comparison of predetermined torsional vibrations produced by the individual cylinders (161, 162, 163, 164, 165, 166), in a fourth step of the method ; the correction factors effect a variation of the amount injected per injection step of the injection pump (61, 62, 63, 64, 65, 66) at least one of these two cylinders.

Description

Die vorliegende Erfindung bezieht sich auf ein Verfahren zum Verbessern des Gleichlaufs einer Hubkolbenbrennkraft­maschine mit volumetrischer Brennstoffzufuhr, im stationä­ren Betriebszustand,mit drei oder mehr Zylindern, sowie einer Hubkolbenbrennkraftmaschine zum Ausüben des Ver­fahrens.The present invention relates to a method for improving the synchronism of a reciprocating piston internal combustion engine with volumetric fuel supply, in the stationary operating state, with three or more cylinders, and a reciprocating piston internal combustion engine for carrying out the method.

Die Steuerung und Ueberwachung des Gleichlaufs derartiger Hubkolbenbrennkraftmaschinen, wie beispielsweise Dieselmo­toren, erfolgt bisher mit der Ueberwachung der Drehzahl der Abtriebswelle oder der Welle einer vom Motor ange­triebenen Maschine. Die Regelung selbst erfolgt über die Aenderung der Einspritzmenge aller Einspritzpumpen, wel­che in enem bestimmten Zyklus den einzelnen Zylindern zugeschaltet werden.The control and monitoring of the synchronism of such reciprocating internal combustion engines, such as diesel engines, has hitherto been carried out by monitoring the speed of the output shaft or the shaft of a machine driven by the engine. The regulation itself is carried out by changing the injection quantity of all injection pumps, which are switched on to the individual cylinders in a certain cycle.

Diese bekannte Art der Regelung berücksichtigt und regelt die Konstanz der Drehzahl in dem Sinne, dass mit der Ver­änderung der Einspritzmenge diese für sämtliche Zylinder in gleicher Weise verändert wird, wenn man davon aus geht, dass die Einspritzmenge in jedem Zylinder gleich gross ist.This known type of regulation takes into account and regulates the constancy of the rotational speed in the sense that with the change in the injection quantity, this is changed in the same way for all cylinders if it is assumed that the injection quantity in each cylinder is the same.

Eine derartige Regelung nimmt keinerlei Rücksicht auf Torsionsschwingungen der Wellen, die somit bei bisher be­kannten Drehzahlregelungen unberücksichtigt bleiben.Such a regulation takes no account of torsional vibrations of the shafts, which are therefore not taken into account in previously known speed controls.

Es gibt Fälle, wo diese Art der Regelung nicht ausreichend ist und bei denen die durch Torsionsschwingungen der Wellen entstehenden Drehzahlunterschiede oder dadurch entstehende Aenderungen der Winkelgeschwindigkeit innerhalb einer Um­drehung schon störend sein können. Beispielsweise kann dieser durch Torsionsschwingungen erzeugte Ungleichlauf in dieselgetriebenen elektrischen Maschinen wie Generato­ren sich störend auswirken. Bei derartigen Anlagen, die etwa mit langsamlaufenden Zweitakt-Dieselmotoren, (z.B. 80 bis l20/Min.) angetrieben werden, liegt in vielen Fällen die Erregungsfrequenz für Torsionsschwingungen erster und zweiter Ordnung der Welle (einfache oder doppel­te Drehfrequenz) in der Nähe der elektrischen Eigenfrequenz des Generators. Dabei kann der Fall eintreten, dass die Amplituden der Torsionsschwingungen dieser Ordnungen dynamisch mehrfach vergrössert werden, wobei im Verbundbe­trieb das mechanische Wellensystem als Ganzes gegen das starre Verbundnetz schwingt, was beispielsweise zu Lei­stungspendelungen führen kann. In einem selbständigen Netz (Inselbetrieb) wiederum kann dies Lichtflimmern zur Folge haben. Die Erfindung schafft hier Abhilfe und gewährleistet ein in dieser Hinsicht wesentlich verbessertes Gleichlaufver­halten der Hubkolbenbrennkraftmaschine. Erfindungsgemäss ist ein derartiges Verfahren zum Verbessern des Gleich­ laufs einer drei- oder mehrzylindrigen Hubkolbenbrenn­kraftmaschine, dadurch gekennzeichnet, dass die Torsions­schwingungen wenigstens einer Ordnung der Antriebswelle minimiert werden, indem der indizierte Zylindermittel­druck wenigstens eines Zylinders verändert wird. Die Er­findung betrifft ferner eine Hubkolbenbrennkraftmaschine zur Ausführung des Verfahrens sowie vorteilhafte besondere Ausführungsformen des Verfahrens bzw. der Hubkolbenbrenn­kraftmaschine.There are cases where this type of control is not sufficient and in which the speed differences resulting from torsional vibrations of the shafts or changes in the angular velocity resulting therefrom can be disruptive within one revolution. For example, this uneven running caused by torsional vibrations in diesel-powered electrical machines such as generators can have a disruptive effect. In systems of this type, which are driven, for example, by slow-running two-stroke diesel engines (e.g. 80 to 120 / min.), The excitation frequency for torsional vibrations of the first and second order of the shaft (single or double rotational frequency) is in many cases close to the electrical natural frequency of the generator. The case may arise in which the amplitudes of the torsional vibrations of these orders are dynamically increased several times, with the mechanical shaft system as a whole vibrating against the rigid network in combined operation, which can lead to power fluctuations, for example. In an independent network (stand-alone operation), this can result in flickering light. The invention provides a remedy here and ensures that the reciprocating piston internal combustion engine has a significantly improved synchronism behavior in this respect. Such a method for improving the same is according to the invention running a three- or multi-cylinder reciprocating internal combustion engine, characterized in that the torsional vibrations of at least one order of the drive shaft are minimized by changing the indicated mean cylinder pressure of at least one cylinder. The invention further relates to a reciprocating piston internal combustion engine for carrying out the method and advantageous special embodiments of the method and the reciprocating piston internal combustion engine.

Die Erfindung wird am Beispiel der Zeichnungen näher er­läutert. Es zeigen:

  • Fig. l schematisch einen sechszylindrigen Die­selmotor mit Generator und erfindungsge­mässer Anlage für die Verbesserung des Gleichlaufs des Dieselmotors,
  • Fig. 2, 2A, 2B und 2C je schematisch einen sechszylindrigen Schiffsdieselmotor mit nebengeschaltetem Bordnetz-Generator und erfindungsgemässer Anlage für die Verbesserung des Gleich­laufs des Dieselmotors,
  • Fig. 3 das Poldiagramm der Torsionsschwingungen erster Ordnung der Welle eines Sechszy­linder-Dieselmotors bzw. einer vom Die­selmotor angetriebenen Welle.
The invention is explained in more detail using the example of the drawings. Show it:
  • 1 schematically shows a six-cylinder diesel engine with generator and system according to the invention for improving the synchronism of the diesel engine,
  • 2, 2A, 2B and 2C each schematically a six-cylinder marine diesel engine with a connected on-board electrical system generator and system according to the invention for improving the synchronism of the diesel engine,
  • 3 shows the pole diagram of the torsional vibrations of the first order of the shaft of a six-cylinder diesel engine or of a shaft driven by the diesel engine.

Der sechszylindrige Zweitakt-Dieselmotor l mit Auflade­gruppe ll und mit der Welle l2 treibt einen Generator 2, wobei der Rotor des Generators, wie gezeichnet, direkt auf der Verlängerung der Welle l2 montiert oder die Rotorwelle mit der Welle l2 des Dieselmotors l gekuppelt sein kann. Die Torsionsschwingungen bzw. deren Amplituden und Winkellage werden mit dem Torsionsschwingungsmesser 3 am Wellenende l23 laufend gemessen und dem Fourier-­Analysator 4 zugeführt. Im Fourier-Analysator 4 wird die Fourierzerlegung der Torsionsschwingungen in die Glieder verschiedener Ordnung durchgeführt.The six-cylinder two-stroke diesel engine l with turbocharger ll and with the shaft l2 drives a generator 2, the rotor of the generator being mounted directly on the extension of the shaft l2 or as shown Rotor shaft can be coupled to the shaft l2 of the diesel engine l. The torsional vibrations or their amplitudes and angular position are measured with the torsional vibration meter 3 measured continuously at the shaft end l23 and fed to the Fourier analyzer 4. In the Fourier analyzer 4, the Fourier decomposition of the torsional vibrations into members of different orders is carried out.

Vorerst spritzen die Einspritzpumpen 6l, 62, 63, 64, 65, 66, von denen je eine einem Zylinder l6l, l62, l63, l64, l65, l66 zugeordnet ist, vorbestimmte, unter sich glei­che Mengen Brennstoff in die Zylinder. Sobald der Diesel­motor den stationären Betriebszustand erreicht hat, wird der Schalter 45 geschlossen, und die Fouriersignale des Fourier-Analysators gelangen nun zur Einspritzpumpen-­Steuerung 5, welche einen Rechner umfasst, der aufgrund beispielsweise der Glieder erster und zweiter Ordnung nach z.B. der Kurbelsternmethode, die anhand von Fig. 3 erklärt wird, bestimmt:

  • 1. welcher oder welche der Zylinder l6l, l62, l63, l64, l65, l66, die Anregung der Torsionsschwingungen dieser Ordnung verursachen,
    und
  • 2. welche Korrektur der Einspritzmenge in welchen Zylindern erforderlich ist, um die Torsionsschwingungen dieser Ordnung zu minimieren.
For the time being, the injection pumps 6l, 62, 63, 64, 65, 66, each of which is assigned to a cylinder l6l, l62, l63, l64, l65, l66, spray predetermined, identical amounts of fuel into the cylinders. As soon as the diesel engine has reached the steady-state operating state, the switch 45 is closed and the Fourier signals of the Fourier analyzer now arrive at the injection pump controller 5, which comprises a computer which, for example, uses the first and second order terms according to the crank star method, for example 3 is determined, determines:
  • 1. which cylinder or cylinders l6l, l62, l63, l64, l65, l66 cause excitation of the torsional vibrations of this order,
    and
  • 2. Which correction of the injection quantity in which cylinders is required in order to minimize the torsional vibrations of this order.

Da es sich bei der Kurbelsternmethode beispielsweise um ein einfaches Näherungsverfahren handelt, erfolgt die Mini­mierung der Torsionsschwingungen iterativ, d.h. in mehreren Zyklen oder Schritten. Bei jedem Schritt werden Korrektur­signale erzeugt, die den betreffenden Einspritzpumpen 6l, 62, 63, 64, 65, 66 zugeführt werden. Aufgrund der Korrek­turen stellt sich im Lauf des Dieselmotors l ein neuer stationärer Zustand ein. Nachdem dieser erreicht ist, werden in einem weiteren Regelzyklus wieder die Torsions­schwingungen gemessen und analysiert und aufgrund der Analyseergebnisse andere Korrektursignale erzeugt und die Torsionsschwingungen weiter minimiert.Since the crank star method is a simple approximation method, for example, the torsional vibrations are minimized iteratively, ie in several cycles or steps. At each step, correction signals are generated which are fed to the relevant injection pumps 61, 62, 63, 64, 65, 66. Due to the corrections, a new steady state is established in the course of the diesel engine 1. After this is reached the torsional vibrations are measured and analyzed again in a further control cycle and other correction signals are generated on the basis of the analysis results and the torsional vibrations are further minimized.

In der Regel wird ein günstiger stationärer Betriebszu­stand mit minimalen, nicht mehr störenden Torsionsschwin­gungen z.B. erster und zweiter Ordnung der Welle l2 oder auch höherer Ordnungen, nach einigen Regelzyklen der be­schriebenen Art erreicht.As a rule, a favorable steady-state operating condition with minimal torsional vibrations that are no longer disruptive, e.g. first and second order of wave l2 or higher orders, achieved after a few control cycles of the type described.

Der Regelzyklus erstreckt sich dabei mit Vorteil über die Zeit mehrerer Arbeitszyklen (Umdrehungen) des Dieselmotors l. Damit wird erreicht, dass die stochastischen Aenderungen des indizierten Zylindermitteldrucks von Zündung zu Zün­dung der einzelnen Zylinder l6l, l62, l63, l64, l65, l66, das auszuwertende Torsionsschwingungssignal nur in ver­nachlässigbarer Weise beeinträchtigen.The control cycle advantageously extends over the time of several working cycles (revolutions) of the diesel engine 1. It is thus achieved that the stochastic changes in the indicated cylinder mean pressure from ignition to ignition of the individual cylinders 16l, 1662, 1663, 1664, 1665, 1666 only negligibly affect the torsional vibration signal to be evaluated.

Für die Erfassung der Torsionsschwingungen eignet sich z.B. eine unter der Bezeichnung Winkelkodierer (optical incremental encoder, Typ G 70 der Firma Litton) im Markt erhältliche Vorrichtung. Eine Einspritzpumpe, die sich für die Aenderung der Einspritzmenge eignet, ist z.B. in der DE-OS 3l 00 725.2-l3 beschrieben. Fourier-Analysa­toren sind ebenfalls bekannt und im Handel erhältlich (z.B. CAT 25l5 der Firma Genrad).For the detection of the torsional vibrations e.g. a device available on the market under the name angle encoder (optical incremental encoder, type G 70 from Litton). An injection pump that is suitable for changing the injection quantity is e.g. described in DE-OS 3l 00 725.2-l3. Fourier analyzers are also known and commercially available (e.g. CAT 25l5 from Genrad).

Der Zweitakt-Dieselmotor l von Fig. 2 mit den sechs Zylin­dern l6l bis l66 treibt über die Welle 22 den Schiffsan­triebspropeller 7. Das andere Ende der Kurbelwelle 22 des Dieselmotors ist über eine Kupplung l8 mit einem Ueber­setzungsgetriebe 8 verbunden, welches eine hydraulische Pumpe 8l antreibt. Diese Pumpe 8l ist ein Teil eines hydrostatischen Getriebes, das zusammen mit dem hydro­statischen Motor 82 einen geschlossenen hydraulischen Druckmittelkreislauf bildet. Die Versorgung dieses Kreis­laufs mit hydrostatischem Druckmittel, z.B. Oel erfolgt durch die Niederdruckstation 83, die ein Druckmittel­reservoir, eine Zubringerpumpe, eine Ueberströmleitung mit Ueberströmventil, Filter usw. enthält. Der hydrosta­tische Motor 82 treibt über eine Welle 89 den elektri­schen Generator 9. Die Drehzahl der Welle 89 und damit des Generators 9, wird mit dem Messfühler 84 überwacht, von welchem der gemessene Ist-Wert dem Drehzahl-Regler 85 zugeführt, und in welchem der Ist-Wert mit dem vorgegebenen Soll-Wert verglichen wird. Der Generator 9 gibt die elek­trische Energie an das Bordnetz l00 ab. Bei Abweichungen von Ist- und Soll-Wert wird die Menge des den hydrostati­schen Motor 82 durchströmenden Druckmittels verändert, indem die Reglersignale über die Signalleitung 86, einem Stellorgan im Motor 82 zugeführt werden. In diesem Beispiel misst der Torsionsschwingungsmesser 3 die Torsions­schwingungen der Welle des Generators 9. Die Bestimmung der Korrektursignale, welche den Einspritzpumpen 6l, 62, 63, 64, 65, 66 zugeführt werden, werden in gleicher Weise, wie oben für die Anlage von Fig. l beschrieben, bestimmt. Die vom Dieselmotor l erzeugten Torsionsschwingungen, werden über den hydrostatischen Kreislauf auf den Motor 82 und die Welle des Generators teilweise übertragen.The two-stroke diesel engine l from FIG. 2 with the six cylinders l6l to l66 drives the ship propeller 7 via the shaft 22. The other end of the crankshaft 22 of the diesel engine is connected via a clutch l8 to a transmission gear 8 which drives a hydraulic pump 8l . This pump 8l is part of a hydrostatic transmission, which forms a closed hydraulic pressure medium circuit together with the hydrostatic motor 82. This circuit is supplied with hydrostatic pressure medium, for example oil, through the low-pressure station 83, which contains a pressure medium reservoir, a feed pump, an overflow line with overflow valve, filter, etc. The hydrostatic motor 82 drives the electric generator 9 via a shaft 89. The speed of the shaft 89 and thus of the generator 9 is monitored by the sensor 84, from which the measured actual value is fed to the speed controller 85 and in which the Actual value is compared with the specified target value. The generator 9 delivers the electrical energy to the vehicle electrical system 100. In the event of deviations from the actual and target values, the amount of pressure medium flowing through the hydrostatic motor 82 is changed by the controller signals being fed via the signal line 86 to an actuator in the motor 82. In this example, the torsional vibration meter 3 measures the torsional vibrations of the shaft of the generator 9. The determination of the correction signals which are fed to the injection pumps 6l, 62, 63, 64, 65, 66 are carried out in the same way as for the system from FIG. l described, determined. The torsional vibrations generated by the diesel engine 1 are partially transmitted to the engine 82 and the shaft of the generator via the hydrostatic circuit.

Bei der in Fig. 2A dargestellten Schiffsdieselanlage,treibt die Welle l7 des Dieselmotors l,über die Kupplung 7l und Welle 73 den verstellbaren Schiffsantriebspropeller 72. Die Welle l7ʹ des Dieselmotors l, auf der anderen Seite des Dieselmotors, treibt über ein Getriebe 9l den Genera­tor 9, der den elektrischen Strom an das Bordnetz l00 ab­gibt. Die Torsionsschwingungen bzw. deren Amplituden und Winkellage werden mit dem Torsionsschwingungsmesser 3, an der Welle des Generators 9 gemessen und laufend dem Fourier-Analysator 4 zugeführt. Im Fourier-Analysator 4 wird die Fourier-Zerlegung der Torsionsschwingungen in die Glieder verschiedener Ordnung durchgeführt. Die Korrek­tursignale für die Veränderung der Einspritzmenge der Ein­spritzpumpen 6l, 62, 63, 64, 65, 66, werden in der Ein­spritzpumpen-Steuerung 5, welche einen Rechner umfasst, aufgrund beispielsweise der Glieder erster und zweiter Ordnung z.B. nach der Kurbelsternmethode, die anhand von Fig. 3 erklärt wird, bestimmt.In the marine diesel system shown in FIG. 2A, the shaft l7 of the diesel engine 1 drives the adjustable ship propeller 72 via the coupling 7l and shaft 73. The shaft l7ʹ of the diesel engine l, on the other side of the diesel engine, drives the generator via a transmission 9l 9, which delivers the electrical current to the vehicle electrical system 100. The torsional vibrations and their amplitudes and Angular positions are measured with the torsional vibration meter 3 on the shaft of the generator 9 and continuously fed to the Fourier analyzer 4. In the Fourier analyzer 4, the Fourier decomposition of the torsional vibrations into members of different orders is carried out. The correction signals for the change in the injection quantity of the injection pumps 6l, 62, 63, 64, 65, 66 are in the injection pump controller 5, which includes a computer, for example on the basis of the elements of the first and second order, for example according to the crank star method, which is based on Fig. 3 is explained.

Bei der in Fig. 2B dargestellten Schiffsdieselanlage,treibt die Welle l7 des Dieselmotors, über die Kupplung 7l die Welle 73 mit dem verstellbaren Schiffsantriebspropeller 72. Das Getriebe 92 ist als Nebengetriebe an der Welle des Dieselmotors l angeschlossen und treibt über eine Kupplung 94 den Generator 9. Der Generator 9 liefert elektrische Energie an das Bordnetz l00. Auch hier werden die Torsions­schwingungen der Welle des Generators 9 mit dem Torsions­schwingungsmesser 3 nach Amplitude und Winkellage dauernd bestimmt und dem Fourier-Analysator 4 zugeführt. Auch hier erfolgt im Fourier-Analysator 4 die Zerlegung der Torsions­schwingungen in die Glieder verschiedener Ordnung.In the marine diesel system shown in FIG. 2B, the shaft l7 of the diesel engine drives, via the clutch 71, the shaft 73 with the adjustable marine propeller 72. The gear 92 is connected as a secondary gear to the shaft of the diesel engine 1 and drives the generator via a clutch 94 9. The generator 9 supplies electrical energy to the vehicle electrical system 100. Here too, the torsional vibrations of the shaft of the generator 9 are continuously determined with the torsional vibration meter 3 according to their amplitude and angular position and fed to the Fourier analyzer 4. Here, too, the torsional vibrations are broken down into links of different orders in the Fourier analyzer 4.

Bei der in Fig. 2C dargestellten Schiffsdieselanlage, treibt die Welle l7 des Dieselmotors l, über die Kupplung 7l die Welle 73 mit den verstellbaren Schiffsantriebspropeller 72. In dieser Anlage wird das Getriebe 93 direkt von der Welle 73 angetrieben und treibt seinerseits, über die Kupplung 94, den Generator 9. Der Generator 9 liefert elektrische Ener­gie an das Bordnetz l00. Wiederum werden an der Welle des Generators 9 Amplitude und Winkellage der Torsions­schwingungen laufend gemessen und dem Fourier-Analysator 4 zugeführt. Im Fourier-Analysator 4 erfolgt die Fourier-­Zerlegung der Torsionsschwingungen in die Glieder ver­schiedener Ordnung. Die Bestimmung der Korrektursignale für die Einspritzpumpen 6l, 62, 63, 64, 65 und 66 kann bei den Anlagen von Fig. 2A, 2B und 2C in gleicher Weise, wie zu Fig. l beschrieben, erfolgen.In the marine diesel system shown in FIG. 2C, the shaft l7 of the diesel engine 1 drives the shaft 73 with the adjustable ship propeller 72 via the clutch 71. In this system the gear 93 is driven directly by the shaft 73 and in turn drives via the clutch 94, the generator 9. The generator 9 supplies electrical energy to the vehicle electrical system 100. Again, the amplitude and angular position of the torsional vibrations are continuously measured on the shaft of the generator 9 and the Fourier analyzer 4 fed. In the Fourier analyzer 4, the Fourier decomposition of the torsional vibrations into members of different orders takes place. The correction signals for the injection pumps 61, 62, 63, 64, 65 and 66 can be determined in the systems of FIGS. 2A, 2B and 2C in the same way as described for FIG. 1.

Die Verbesserung des Gleichlaufs des Dieselmotors l und auch der vom Dieselmotor angetriebenen Generatoren 9 er­fordert, dass sich der Dieselmotor im wesentlichen in einem stationären Betriebszustand befindet. Dies ist bei Schiffsdieselan­lagen allgemein, und vermehrt noch bei Schiffsdieselan­lagen mit verstellbaren Schiffsantriebspropeller, im Fahr­betrieb über grössere Zeiträume der Fall. Die hydraulischen oder mechanischen Getriebe 9l, 92, 93 vermögen beispiels­weise die Drehzahl des Rotors 9 innerhalb gewisser Grenzen von Drehzahländerungen, wie dies bei Schiffsantrieben mit nichtverstellbarem Schiffsantriebspropeller der Fall sein kann, konstant zu halten. Da ein Schiff über mehrere Bord­generatoren verfügt, wird häufig die vom Antriebsdiesel­motor getriebene Gruppe dem Bordnetz nur im Fahrbetrieb auf offener See, wo der Antriebsmotor mit konstanter Dreh­zahl läuft, zugeschaltet.Improving the synchronism of the diesel engine 1 and also the generators 9 driven by the diesel engine requires that the diesel engine is essentially in a stationary operating state. This is generally the case with marine diesel systems, and increasingly with marine diesel systems with adjustable marine propellers, when operating for longer periods. The hydraulic or mechanical transmissions 91, 92, 93 are able, for example, to keep the speed of the rotor 9 constant within certain limits of speed changes, as can be the case with ship drives with a non-adjustable ship propeller. Since a ship has several on-board generators, the group driven by the drive diesel engine is often only connected to the on-board electrical system when driving on the open sea, where the drive engine runs at constant speed.

Es ist auch möglich, den Rotor des Generators 9 direkt auf die Welle 73 zu setzen und den Generator für eine bestimmte Drehzahl auszulegen, die der Drehzahl des Dieselmotors bei Dauerbetrieb entspricht. Damit würde dann beispielsweise in einer Anlage, wie in Fig. 2C dargestellt, das Getriebe 93 und die Kupplung 94 entfallen. Die Torsionsschwingungen würden in diesem Falle mit dem Torsionsschwingungsmesser 3 an der Welle 73, oder an der Welle l7 gemessen.It is also possible to place the rotor of the generator 9 directly on the shaft 73 and to design the generator for a specific speed which corresponds to the speed of the diesel engine during continuous operation. The transmission 93 and the clutch 94 would then be omitted, for example in a system, as shown in FIG. 2C. In this case, the torsional vibrations would be measured with the torsional vibration meter 3 on the shaft 73, or on the shaft 17.

Anhand von Fig. 3 wird die Kurbelsternmethode für die Be­stimmung der Korrekturfaktoren zur Korrektur der Ein­spritzmenge für die Minimierung der Torsionsschwingungen erster Ordnung erläutert. Im Kurbelsternverfahren geht man beispielsweise von den vereinfachenden Annahmen aus, dass
- der mittlere indizierte Zylinderdruck eines Zylinders nicht mehr als 5 % vom Soll-Wert abweicht.

- sich die Störamplitude linear mit der Störung ändert und die Phase gleich bleibt.

- die gemessene Störung, d.h. eine gemessene Torsions­schwingung durch Korrektur des mittleren indizierten Zylinderdrucks von zwei oder in Sonderfällen einem Zylinder minimiert werden kann, d.h. die Störung durch die entsprechenden Zylinder erzeugt wird.3, the crank star method for determining the correction factors for correcting the injection quantity for minimizing the torsional vibrations of the first order is explained. In the crank star method, for example, the simplifying assumptions are made that
- The average indicated cylinder pressure of a cylinder does not deviate from the target value by more than 5%.

- The disturbance amplitude changes linearly with the disturbance and the phase remains the same.

- The measured disturbance, ie a measured torsional vibration can be minimized by correcting the mean indicated cylinder pressure of two or, in special cases, one cylinder, ie the disturbance is generated by the corresponding cylinder.

Die Zündfolge des Motors sei l, 6, 2, 4, 3, 5. Im Pol­diagramm l9 sind die berechneten Torsionsschwingungsvekto­ren l9l bis l96, erster Ordnung der Welle eines sechszylindri­gen Motors für alle sechs Fälle, dass einer der Zylinder eine 5 %ige Reduktion des mittleren indizierten Zylinder­drucks erbringt, gestrichelt eingezeichnet. Diese Vektoren l9l bis l96 bilden den sogenannten Korrekturkurbelstern erster Ordnung. Die Enden dieser Vektoren l9l bis l96 liegen auf einem Kreis, dessen Mittelpunkt M nicht im Nullpunkt P des Poldiagramms liegt, sondern um einen Vektor l90 ver­schoben ist. Dieser Vektor l90 entspricht dem Torsions­schwingungsvektor des idealen, d.h. vollständig ausge­glichenen Motors.The firing order of the engine is l, 6, 2, 4, 3, 5. In the pole diagram l9 are the calculated torsional vibration vectors l9l to l96, first order of the shaft of a six-cylinder engine for all six cases that one of the cylinders has a 5% reduction in the yields mean indicated cylinder pressure, shown in dashed lines. These vectors l9l to l96 form the so-called first-order correction crank stars. The ends of these vectors l9l to l96 lie on a circle whose center M is not in the zero point P of the pole diagram, but is shifted by a vector l90. This vector l90 corresponds to the torsional vibration vector of the ideal, i.e. fully balanced engine.

Subtrahiert man von den einzelnen Vektoren l9l bis l96 je diesen Vektor l90, so erhält man den verschobenen Korrektur­kurbelstern l9lʹ bis l96ʹ.If you subtract this vector l90 from the individual vectors l9l to l96, you get the shifted correction crank star l9lʹ to l96ʹ.

Dieser berechnete Kurbelstern l9lʹ bis l96ʹ dient nun für die Bestimmung der Korrekturen des mittleren indizierten Zylinderdrucks in einem oder zwei Zylindern.This calculated crank star l9lʹ to l96ʹ is now used to determine the corrections to the mean indicated cylinder pressure in one or two cylinders.

Wird nun beispielsweise an der Welle eine Torsionschwingung S (Amplitude und Phase) gemessen und der Vektor in den ver­schobenen Korrekturkurbelstern eingezeichnet, so liegt S zwischen zwei Vektoren des verschobenen Korrekturkurbel­sterns, in unserem Beispiel zwischen den Vektoren l9lʹ und l96ʹ, oder fällt in die Richtung eines der Vektoren l9lʹ bis l96ʹ. Die Zerlegung des Amplituden-Vektors S in die beiden Vektoren S₁ und S₆ in Richtung der beiden Vektoren des Korrekturkurbelsterns, wird also als Störung der beiden Zylinder l und 2 interpretiert. Da der Korrek­turkurbelstern auf der Annahme von Minderleistungen der gestörten Zylinder basiert, aber die Zylinder auch zuviel leisten könnten, muss diese Zerlegung in der richtigen Vektorbasis gerechnet werden. Diese Basis ist ein Paar aus den Vektoren Z₁, Z₆, Z₃ und Z₄. Der Korrekturfaktor für die zwei Zylinder einer Paarkombination ergibt sich somit direkt aus dem Korrekturkurbelstern.If, for example, a torsional vibration S (amplitude and phase) is measured on the shaft and the vector is drawn in the shifted correction crank star, S lies between two vectors of the shifted correction crank star, in our example between the vectors l9lʹ and l96ʹ, or falls in the direction of one of the vectors l9lʹ to l96ʹ. The decomposition of the amplitude vector S into the two vectors S₁ and S₆ in the direction of the two vectors of the correction crank star is interpreted as a disturbance of the two cylinders 1 and 2. Since the correction crank star is based on the assumption of underperformance of the disturbed cylinders, but the cylinders could also perform too much, this decomposition must be calculated in the correct vector basis. This base is a pair of the vectors Z₁, Z₆, Z₃ and Z₄. The correction factor for the two cylinders of a pair combination thus results directly from the correction crank star.

In Wirklichkeit können einer, oder mehrere Zylinder ge­stört sein. Die vereinfachte Annahme, jede Störung auf beispielsweise zwei gestörte Zylinder zurückzuführen, macht es in der Regel notwendig, die Minimierung iterativ, d.h. in mehreren Schritten durchzuführen. Ein einziger Korrekturfaktor für nur einen Zylinder ergibt sich dann, wenn der Vektor der gemessenen Störung mit einem der Vektoren l9lʹ bis l96ʹ zusammenfällt.In reality, one or more cylinders can be disturbed. The simplified assumption that each fault can be attributed to two faulty cylinders, for example, usually makes it necessary to iteratively minimize the to carry out in several steps. A single correction factor for only one cylinder is obtained if the vector of the measured disturbance coincides with one of the vectors l9lʹ to l96ʹ.

Obschon die Berechnung der Korrekturfaktoren für die Stö­rungen erster Ordnung hier aus Gründen der Anschaulichkeit an einem graphischen Beispiel erläutert wurde, ist es zwecksmässig, die Korrekturfaktoren in der Einspritzpumpen­steuerung 5 rechnerisch, d.h. numerisch zu ermitteln. In analoger Weise können auch die Korrekturfaktoren für die Minimierung der Torsionsschwingungen zweiter Ordnung be­stimmt werden.Although the calculation of the correction factors for the disturbances of the first order was explained here for the sake of clarity using a graphic example, it is useful to determine the correction factors in the injection pump control 5 arithmetically, ie numerically. In The correction factors for minimizing the second-order torsional vibrations can also be determined analogously.

Die beschriebene Art der Minimierung der Torsionsschwin­gungen hat sich in der Praxis als sehr günstig erwiesen. Die Erfindung ist keineswegs auf die beschriebenen Aus­führungsbeispiele beschränkt, sondern umfasst irgend­welche Verfahren zur Verbesserung des Gleichlaufs von Hubkolbenbrennkraftmaschinen, bei denen auf den indizier­ten Mitteldruck einwirkende Korrekturfaktoren in anderer Weise ermittelt werden.The described way of minimizing the torsional vibrations has proven to be very favorable in practice. The invention is in no way limited to the exemplary embodiments described, but rather comprises any method for improving the synchronism of reciprocating piston internal combustion engines, in which correction factors acting on the indicated medium pressure are determined in a different way.

Die Erfindung wurde anhand von Beispielen, die sich auf Dieselmotoren beziehen erläutert. Prinzipiell ist das Verfahren aber für jede Hubkolbenbrennkraftmaschine mit volumetrischer Brennstoffzufuhr zu den Zylindern anwendbar.The invention has been explained on the basis of examples relating to diesel engines. In principle, however, the method can be used for any reciprocating piston internal combustion engine with volumetric fuel supply to the cylinders.

Claims (13)

1. Verfahren zum Verbessern des Gleichlaufs einer drei- ­oder mehrzylindrigen Hubkolbenbrennkraftmaschine im stationären Betriebszustand, dadurch gekenn­zeichnett, dass die Torsionsschwingungen wenigstens einer Ordnung der Antriebswelle (l2, 22) minimiert werden, indem der indizierte Zylindermittel­druck und damit die anregenden Momente wenigstens eines Zylinders (l6l, l62, l63, l64, l65, l66) verändert werden.1.Method for improving the synchronism of a three- or multi-cylinder reciprocating piston internal combustion engine in the stationary operating state, characterized in that the torsional vibrations of at least one order of the drive shaft (l2, 22) are minimized by the indicated cylinder mean pressure and thus the exciting moments of at least one cylinder (l6l , l62, l63, l64, l65, l66) can be changed. 2. Verfahren nach Anspruch l, dadurch gekennzeichnet, dass der indizierte Zylindermitteldruck durch Verändern der Einspritzmenge verändert wird.2. The method according to claim l, characterized in that the indicated cylinder mean pressure is changed by changing the injection quantity. 3. Verfahren nach Anspruch 2, dadurch gekennzeichnet, dass die Torsionsschwingungen der Antriebswelle oder einer mit ihr gekoppelten weiteren Welle (l2, 22) mit einer Torsionsschwingungs-Messvorrichtung (3) laufend ge­messen wird, dass die Fourier-Analyse der Torsions­schwingungen ermittelt wird, und dass in einem Rechner (5) aus Betrag und Phase der Torsionsschwingungsampli­tude verschiedener Ordnung Korrekturfaktoren für die Veränderung des indizierten Zylindermitteldrucks minde­stens zweier Zylinder bestimmt werden, und dass diese Korrekturfaktoren die Einspritzmenge pro Einspritzvor­gang der Einspritzpumpe (6l, 62, 63, 64, 65, 66) mindestens einer dieser zwei Zylinder ändert.3. The method according to claim 2, characterized in that the torsional vibrations of the drive shaft or a further shaft coupled to it (l2, 22) is continuously measured with a torsional vibration measuring device (3), that the Fourier analysis of the torsional vibrations is determined, and that correction factors for changing the indicated cylinder mean pressure of at least two cylinders are determined in a computer (5) from the amount and phase of the torsional vibration amplitude of different orders, and that these correction factors determine the injection quantity per injection process of the injection pump (6l, 62, 63, 64, 65, 66 ) changes at least one of these two cylinders. 4. Verfahren nach Anspruch l, 2 oder 3, dadurch gekenn­zeichnet, dass die Torsionsschwingungen erster und zweiter Ordnung minimiert werden.4. The method according to claim 1, 2 or 3, characterized in that the torsional vibrations of the first and second order are minimized. 5. Verfahren nach einem der Ansprüche l bis 4, dadurch ge­kennzeichnet, dass die Minimierung der Torsionsschwin­gungen iterativ, in mehreren Schritten erfolgt.5. The method according to any one of claims 1 to 4, characterized in that the torsional vibrations are minimized iteratively in several steps. 6. Verfahren nach einem der Ansprüche l bis 5, dadurch ge­kennzeichnet, dass die Torsionsschwingungen an der Welle (l23) eines elektrischen Generators (2, 9; 9l, 92, 93), welche von der Welle (l2) der Hubkolbenbrennkraft­maschine (l) direkt oder über ein Getriebe (8, 8l, 82, 83) angetrieben ist, oder welche eine Verlängerung (l23) der Welle (l2) der Hubkolbenbrennkraftmaschine ist, ge­messen wird, und dass mit der Minimierung der Torsions­schwingungen der Generatorwelle (l23, 89) auch die Tor­sionsschwingungen der Welle (l2) der Hubkolbenbrenn­kraftmaschine minimiert werden.6. The method according to any one of claims l to 5, characterized in that the torsional vibrations on the shaft (l23) of an electric generator (2, 9; 9l, 92, 93) which of the shaft (l2) of the reciprocating piston internal combustion engine (l) is driven directly or via a gear (8, 81, 82, 83), or which is an extension (l23) of the shaft (l2) of the reciprocating piston internal combustion engine, is measured, and that with the minimization of the torsional vibrations of the generator shaft (l23, 89) the torsional vibrations of the shaft (l2) of the reciprocating piston internal combustion engine can also be minimized. 7. Hubkolbenbrennkraftmaschine zur Ausübung des Verfahrens nach Anspruch l, gekennzeichnet durch eine Vorrichtung (3) zum Messen der Torsionsschwingungen der Antriebs­welle oder einer mit dieser gekoppelten weiteren Welle, durch einen Fourier-Analysator (4), dem die Torsions­schwingungs-Messwerte zugeführt werden, durch einen Rechner (5), der aus Phase und Amplitude von Gliedern der Fourier-Analyse, Korrektursignale für die Kraft­stoff-Einspritzmenge wenigstens eines Zylinders bestimmt und einer Einspritzvorrichtung (6l, 62, 63, 64, 65, 66), welcher die Korrektursignale zugeführt werden, und wel­che die aufgrund der Korrektursignale veränderte Kraft­stoffmenge in die Zylinder eingespritzt und damit den indizierten Zylindermitteldruck dieser Zylinder ändert.7. Reciprocating piston internal combustion engine for carrying out the method according to claim 1, characterized by a device (3) for measuring the torsional vibrations of the drive shaft or a further shaft coupled thereto, by a Fourier analyzer (4), to which the torsional vibration measured values are supplied a computer (5) which determines from the phase and amplitude of elements of the Fourier analysis, correction signals for the fuel injection quantity of at least one cylinder and an injection device (61, 62, 63, 64, 65, 66) to which the correction signals are supplied , and which injects the amount of fuel changed due to the correction signals into the cylinders and thus changes the indicated mean cylinder pressure of these cylinders. 8. Hubkolbenbrennkraftmaschine nach Anspruch 7, dadurch gekennzeichnet, dass diese 3 bis l2 Zylinder aufweist.8. Reciprocating internal combustion engine according to claim 7, characterized in that it has 3 to l2 cylinders. 9. Hubkolbenbrennkraftmaschine nach Anspruch 7 oder 8, dadurch gekennzeichnet, dass diese ein langsamlaufen­der Zweitakt-Dieselmotor ist.9. Reciprocating internal combustion engine according to claim 7 or 8, characterized in that it is a slow-running two-stroke diesel engine. l0. Hubkolbenbrennkraftmaschine nach einem der Ansprüche 7 bis 9, dadurch gekennzeichnet, dass eine axiale Verlängerung der Welle der Hubkolbenbrennkraftmaschi­ne als Welle eines elektrischen Generators ausgebildet ist und die Vorrichtung (3) zum Messen der Torsions­schwingungen derart angeordnet ist, dass die Torsions­schwingungen der Generatorwelle (l23) misst.l0. Reciprocating piston internal combustion engine according to one of claims 7 to 9, characterized in that an axial extension of the shaft of the reciprocating piston internal combustion engine is designed as a shaft of an electrical generator and the device (3) for measuring the torsional vibrations is arranged such that the torsional vibrations of the generator shaft (I23) measure . 11. Hubkolbenbrennkraftmaschine nach einem der Ansprüche 7 bis l0, dadurch gekennzeichnet, dass zwischen der Hauptwelle (l2) der Hubkolbenbrennkraftmaschine (l) und einer Nebenwelle (89) ein Getriebe (8, 8l, 82, 83; 9l, 92, 93) angeordnet ist, und dass die Vorrichtung (3) zum Messen der Torsionsschwingungen derart angeordnet ist, dass die Torsonsschwingungen der Nebenwelle (9, 89) misst.11. Reciprocating internal combustion engine according to one of claims 7 to 10, characterized in that a gear (8, 8l, 82, 83; 9l, 92, 93) is arranged between the main shaft (l2) of the reciprocating internal combustion engine (l) and a secondary shaft (89) and that the device (3) for measuring the torsional vibrations is arranged such that the torsional vibrations of the auxiliary shaft (9, 89) measure. 12. Hubkolbenbrennkraftmaschine nach einem der Ansprüche 7 bis ll, dadurch gekennzeichnet, dass ein gemeinsamer Rechner für die Fourier-Analyse der Torsionsschwingungen und die Bestimmung des Korrektursignals für die Ver­änderung des Einspritzvorgangs der Einspritzvorrich­tung (6l, 62, 63, 64, 65, 66) vorhanden ist.12. reciprocating piston internal combustion engine according to one of claims 7 to ll, characterized in that a common computer for the Fourier analysis of the torsional vibrations and the determination of the correction signal for changing the injection process of the injection device (6l, 62, 63, 64, 65, 66) is available. 13. Hubkolbenbrennkraftmaschine nach einem der Ansprüche 7 bis l2, dadurch gekennzeichnet, dass zwischen der Hauptwelle (l2) der Hubkolbenbrennkraftmaschine (l) und einer Nebenwelle ein Getriebe angeordnet ist, und dass die Vor­richtung zum Messen der Torsionsschwingungen derart angeordnet ist, dass sie die Torsionsschwingungen der Nebenwelle (9, 89) misst.13. Reciprocating piston internal combustion engine according to one of claims 7 to l2, characterized in that between the main shaft (l2) of the reciprocating piston internal combustion engine (l) and a secondary shaft, a transmission is arranged, and that the device for measuring the torsional vibrations is arranged in such a way that the torsional vibrations the auxiliary shaft (9, 89).
EP19870108248 1986-06-23 1987-06-06 Method for the improvement of the regularity with a piston engine and engine running according to this method Expired - Lifetime EP0254005B1 (en)

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CH252486A CH674398A5 (en) 1986-06-23 1986-06-23
CH2524/86 1986-06-23

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EP (1) EP0254005B1 (en)
JP (1) JP2686261B2 (en)
CH (1) CH674398A5 (en)
DE (1) DE3761577D1 (en)
DK (1) DK162853C (en)
FI (1) FI89404C (en)

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Publication number Priority date Publication date Assignee Title
EP0447697A2 (en) * 1990-03-23 1991-09-25 Mitsubishi Jukogyo Kabushiki Kaisha Apparatus for suppressing torsional vibration of a crank shaft of a diesel engine
WO1994029580A1 (en) * 1993-06-04 1994-12-22 Man B & W Diesel A/S Internal combustion engine
EP0710841A2 (en) * 1994-11-07 1996-05-08 Eaton Corporation Driveline vibration analyzer
WO2000055484A1 (en) * 1999-03-12 2000-09-21 Continental Isad Electronic Systems Gmbh & Co. Ohg Device for damping irregularities in the drive train of a motor vehicle driven by a combustion engine
EP1435446A2 (en) * 2003-01-02 2004-07-07 FERRARI S.p.A. Method of reducing resonance phenomena in a transmission train of a vehicle internal combustion engine
WO2005124132A1 (en) * 2004-06-17 2005-12-29 Man B & W Diesel A/S Vibration reduction in large diesel engines
US7082932B1 (en) * 2004-06-04 2006-08-01 Brunswick Corporation Control system for an internal combustion engine with a supercharger
EP1739296A1 (en) * 2005-06-30 2007-01-03 Wärtsilä Schweiz AG Method to optimise an operating parameter of a reciprocating combustion engine, and engine
CN115031978A (en) * 2022-04-07 2022-09-09 哈尔滨工程大学 Diesel engine crankshaft torsional vibration model calibration method based on transient stress of connecting rod
CN115217664A (en) * 2021-06-07 2022-10-21 广州汽车集团股份有限公司 Cylinder pressure control method and device and storage medium

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FI121150B (en) 2005-11-30 2010-07-30 Waertsilae Finland Oy Apparatus and method for a piston combustion engine for identifying an uneven cylinder power ratio

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EP0113510A2 (en) * 1982-12-09 1984-07-18 General Motors Corporation Diesel fuel injection pump with adaptive torque balance control

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Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0447697A2 (en) * 1990-03-23 1991-09-25 Mitsubishi Jukogyo Kabushiki Kaisha Apparatus for suppressing torsional vibration of a crank shaft of a diesel engine
EP0447697A3 (en) * 1990-03-23 1992-03-04 Mitsubishi Jukogyo Kabushiki Kaisha Apparatus for suppressing torsional vibration of a crank shaft of a diesel engine
WO1994029580A1 (en) * 1993-06-04 1994-12-22 Man B & W Diesel A/S Internal combustion engine
CN1044732C (en) * 1993-06-04 1999-08-18 曼·B及W柴油机公司 Internal combustion engine
EP0710841A2 (en) * 1994-11-07 1996-05-08 Eaton Corporation Driveline vibration analyzer
EP0710841A3 (en) * 1994-11-07 1998-11-18 Dana Corporation Driveline vibration analyzer
WO2000055484A1 (en) * 1999-03-12 2000-09-21 Continental Isad Electronic Systems Gmbh & Co. Ohg Device for damping irregularities in the drive train of a motor vehicle driven by a combustion engine
EP1435446A3 (en) * 2003-01-02 2005-01-26 FERRARI S.p.A. Method of reducing resonance phenomena in a transmission train of a vehicle internal combustion engine
EP1435446A2 (en) * 2003-01-02 2004-07-07 FERRARI S.p.A. Method of reducing resonance phenomena in a transmission train of a vehicle internal combustion engine
US7212900B2 (en) 2003-01-02 2007-05-01 Ferrari S.P.A. Method of reducing resonance phenomena in a transmission train of a vehicle internal combustion engine
US7082932B1 (en) * 2004-06-04 2006-08-01 Brunswick Corporation Control system for an internal combustion engine with a supercharger
WO2005124132A1 (en) * 2004-06-17 2005-12-29 Man B & W Diesel A/S Vibration reduction in large diesel engines
KR100940528B1 (en) * 2004-06-17 2010-02-10 맨 디젤 필리얼 아프 맨 디젤 에스이, 티스크랜드 Vibration reduction in large diesel engines
CN1977099B (en) * 2004-06-17 2010-09-01 曼B与W狄赛尔公司 Crosshead type large piston engine operation method and diesel engines with related structure
EP1739296A1 (en) * 2005-06-30 2007-01-03 Wärtsilä Schweiz AG Method to optimise an operating parameter of a reciprocating combustion engine, and engine
CN115217664A (en) * 2021-06-07 2022-10-21 广州汽车集团股份有限公司 Cylinder pressure control method and device and storage medium
CN115217664B (en) * 2021-06-07 2023-09-29 广州汽车集团股份有限公司 Cylinder pressure control method, device and storage medium
CN115031978A (en) * 2022-04-07 2022-09-09 哈尔滨工程大学 Diesel engine crankshaft torsional vibration model calibration method based on transient stress of connecting rod

Also Published As

Publication number Publication date
EP0254005B1 (en) 1990-01-31
JP2686261B2 (en) 1997-12-08
DK150087A (en) 1987-12-24
FI871638A (en) 1987-12-24
DK162853C (en) 1995-12-04
DK162853B (en) 1991-12-16
JPS6312864A (en) 1988-01-20
FI89404C (en) 1993-09-27
FI89404B (en) 1993-06-15
DE3761577D1 (en) 1990-03-08
CH674398A5 (en) 1990-05-31
FI871638A0 (en) 1987-04-14
DK150087D0 (en) 1987-03-24

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