EP0909883B1 - Arrangement and method for valve driving in a reversible diesel engine - Google Patents

Arrangement and method for valve driving in a reversible diesel engine Download PDF

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Publication number
EP0909883B1
EP0909883B1 EP97810766A EP97810766A EP0909883B1 EP 0909883 B1 EP0909883 B1 EP 0909883B1 EP 97810766 A EP97810766 A EP 97810766A EP 97810766 A EP97810766 A EP 97810766A EP 0909883 B1 EP0909883 B1 EP 0909883B1
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EP
European Patent Office
Prior art keywords
valve
cam
control
arrangement
fuel
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP97810766A
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German (de)
French (fr)
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EP0909883A1 (en
Inventor
Wolfgang Stadlin
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Wartsila NSD Schweiz AG
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Wartsila NSD Schweiz AG
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Application filed by Wartsila NSD Schweiz AG filed Critical Wartsila NSD Schweiz AG
Priority to EP97810766A priority Critical patent/EP0909883B1/en
Priority to DK97810766T priority patent/DK0909883T3/en
Priority to DE59708956T priority patent/DE59708956D1/en
Priority to TW087101840A priority patent/TW360739B/en
Priority to JP10234228A priority patent/JPH11159314A/en
Priority to PL98329104A priority patent/PL329104A1/en
Priority to CNB981213561A priority patent/CN1247881C/en
Priority to KR1019980042753A priority patent/KR100527820B1/en
Publication of EP0909883A1 publication Critical patent/EP0909883A1/en
Application granted granted Critical
Publication of EP0909883B1 publication Critical patent/EP0909883B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/08—Shape of cams
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/02—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for reversing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • F01L9/11—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34446—Fluid accumulators for the feeding circuit
    • 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
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F7/00—Casings, e.g. crankcases or frames
    • F02F2007/0097—Casings, e.g. crankcases or frames for large diesel engines

Definitions

  • the invention relates to an arrangement and a method for valve control of a reversible Diesel engine according to the preamble of respective independent claim.
  • Examples are the fuel and valve cams arranged for the exhaust valve so that the Forward the apex of the exhaust valve cam the fuel cam by a crank angle of 145 ° lags, the reversal results in Direction of rotation (reverse running) that the apex of the Exhaust valve cam that of the fuel cam by one Crank angle lagged by 215 °, so the sequence between fuel injection and Exhaust valve actuation (based on the movement cycle of the piston in the cylinder) no longer that of the Forward running corresponds.
  • the Operating behavior of the internal combustion engine at Reverse run is badly deteriorated.
  • DE-A-31 28 332 therefore proposes that Fuel cams for reversing operation with respect to Twisting the control shaft means the fuel cams can with respect to their angular position on the control shaft can be switched between two positions while the Exhaust valve cams for both directions of rotation of the Control shaft in the same angular position with respect to the Control shaft remain. This measure is ensures that the tax dates for both Rotation directions are optimal.
  • the reversal of the Fuel cams are made by means of hydraulic Reversing devices, the fuel cams with respect to the control shaft from the position for the Twist the forward run into the for the reverse run or vice versa.
  • valve cam controls a valve cam on the Control shaft opening the valve while the Closing the valve is controlled by means that are different from the valve cam.
  • the measure is only one of the flanks per direction of rotation of the valve cam for valve control because for controlling the closing of the valve others Means are provided as in particular the second flank of the valve cam.
  • the valve cam can do so be arranged and designed so that its a Flank the opening of the valve when running forward optimally and regarding fuel injection to the desired time controls while its second Edge for these functions when running backwards responsible for.
  • the arrangement according to the invention or the Methods according to the invention are particularly suitable for Two-stroke large diesel engines such as B. in shipbuilding be used.
  • Fig. 1 shows an illustration of a first Embodiment of the inventive arrangement for Valve control of a reversible - not closer illustrated - diesel engine.
  • the order is generally provided with the reference number 1.
  • she includes one completely reversible and in two Directions rotatable control shaft 2, which in itself known manner from the crankshaft Diesel engine is powered and for both The directions of rotation are synchronous with the crankshaft running.
  • the control shaft 2 is overall with respect to Reversible crankshaft, d. H. when switching from Forward run in reverse, or vice versa the control shaft 2 in total by a reversal angle twisted with respect to the crankshaft and then runs again synchronized with the crankshaft.
  • the phase position of the Control shaft 2 with respect to the crankshaft is therefore for the Forward run is different than for reverse run.
  • the Rerouting the entire tax wave is one in itself known measure, which is therefore not explained in detail here becomes. It is possible, for example, within the Control shaft gear to provide a reversing servo motor, which is designed in the same way as that reversing device described in DE-A-31 28 332 for the fuel cams. Because in the timing shaft gear if there’s enough space, it’s not a problem, to design the reversing servo motor in such a way that moment created him to reverse the whole Control shaft 2 is sufficient.
  • a fuel cam 4 is on the control shaft 2 Control of fuel injection into the combustion chamber of a cylinder, not shown Diesel engine and a valve cam 3 for Control of a valve 5, for example one Exhaust valve 5, the same cylinder provided.
  • the Fuel cam 4 actuates in a manner known per se z.
  • the valve cam 3 actuates a follower roller 6 Stroke pump 7, the working piston 71 in a socket 74 is guided and delimits a working space 72.
  • the Working space 72 is connected to the hydraulic line 8 Exhaust valve 5 connected to this hydraulically actuate.
  • an upward movement a hydraulic medium in the hydraulic line 8 under pressure set, whereby the exhaust valve 5 is opened.
  • the valve cam 3 controls the opening of the Exhaust valve 5.
  • valve cam 3 various means are provided which the closing of valve 5 control.
  • these means include one in the stroke pump provided overflow connection 73 for pressure relief the hydraulic line 8.
  • the overflow connection leads from Working space 72 of the stroke pump 7 to an annular groove 75 in the outer surface of the working piston 71.
  • the bushing 74 there is at least one bore 76 provided in one Ring channel 77 opens out, which the outer wall of the Surrounds sleeve 74 in the circumferential direction.
  • the ring channel 77 is connected to an outlet duct 78 through which the Hydraulic medium, for example an oil, can flow out.
  • the annular groove 75 in the wall of the working piston 71 on the one hand and the bore 76 or the bores 76 in the socket 74, on the other hand, are such relative to one another arranged that they are only connected to each other if the working piston 71 in the area of its upper Dead center is located. With top dead center is there the reversal point of the working piston 71 is meant at which the volume of the working space 72 is minimal.
  • the means include which control the closing of the valve 5, also one Throttle device, e.g. B. a throttle valve 9, to which the outlet duct 78 leads.
  • the throttle valve 9 is used Hydraulic line pressure relief control 8. From the throttle valve 9 extends a return duct 10, the in a supply line 11 for the hydraulic medium empties. The feed line 11 does not lead from one shown reservoir for the hydraulic medium via a check valve 12 and opens into the Hydraulic line 8 a.
  • Fig. 3 shows in a Cross-sectional view of such a valve cam 3.
  • Die The contour of the valve cam 3 comprises a first flank 31 and a second flank 32. Between the two flanks 31, 32, the valve cam 3 has a central region 34 in which its contour is essentially parallel to Base circle 33 runs.
  • this middle Area has the contour of the valve cam 3 two effective vertices S1 and S2, each of which one in the transition area between the first flank 31 and the middle region 34 and in the transition region between the middle region 34 and the second flank 32 lies.
  • “effective vertex” is there that point of the contour of the valve cam 3 is meant, on which the follower roller 6 (Fig. 1) rests when the Opening process of valve 5 has just been completed, d. H. when the valve 5 is just fully open.
  • the follower role 6 is on one of the effective ones Vertices, the working piston 71 is the Stroke pump 7 approximately in its top dead center.
  • the valve cam 3 is designed such that the two effective vertices S1, S2 so arranged are that - regardless of the direction of rotation - each the first vertex S1 or S2 in the direction of rotation relative to the vertex of the fuel cam 4 around the is offset at the same angle.
  • FIG. 2 illustrates the arrangement of the Cam 3,4 on the control shaft 2 in a linearized Presentation.
  • V On the axis V are the crank angles KW for Forward run entered, those for the R axis Reverse.
  • the middle area 34 of the Valve cam has a length d2, the 70 ° KW, that is Reversal angle corresponds.
  • the second effective vertex S2 for the forward run at KW 250 °.
  • Its angular distance d3 to the fuel cam 4 seen in the forward direction (axis V) is thus also 145 °.
  • the throttle valve 9 can be the The closing process or the closing time is checked influence or control. From the throttle valve 9 the flowing hydraulic medium passes through the Return channel 10 into the feed line 11.
  • the closing of the valve 5 is done by relieving the pressure Hydraulic line 8, while during the closing of the Valve 5 of the working piston 71 of the stroke pump 7 through the valve cam 3 in the area of its top dead center is held, that is, the follower role 6 overflows the middle region 34 of the valve cam 3.
  • the working piston 71 moves, for. B. due to a known, not shown Spring load, as shown (Fig. 1) downwards, whereby on the one hand the overflow connection 73 is closed and the other hydraulic medium from the Feed line 11 sucked into the hydraulic line 8 as soon as the pressure in the hydraulic line 8 has dropped that the check valve 12 opens.
  • the first edge 31 of the valve cam 3 serves when running forward and the second edge 32 when Reverse to control the opening of the valve 5 and the valve closes for both directions of rotation 5 by 3 different means from the valve cam controlled with which the pressure relief of the Hydraulic line 8 takes place. Since only per direction of rotation a flank 31 or 32 of the valve cam 3 for the Valve control is required, the two edges 31,32 are pulled apart so that the angular distance d1 or d2 (crank angle difference) of in the direction of rotation front effective vertex S1 or S2 to Vertex of the fuel cam 4 regardless of the Direction of rotation of the control shaft 2 is. This is for both the forward as well as the reverse run of the Diesel engine an optimal operating behavior guaranteed, especially with regard to the Interaction between fuel injection and Valve actuation.
  • Fig. 4 shows a variant in a sectional view for the design of the valve cam 3. Also at this variant is the contour of the valve cam between the two effective vertices S1, S2, i.e. in middle area 34, different from the base circle, but does not run parallel to the base circle 33, but has a minimum.
  • This measure can Amount of hydraulic medium required to close valve 5 must flow out, be reduced.
  • the minimum namely the working piston 71 (FIG. 1) of the stroke pump 7 slightly - as shown - moved down. However, this movement is of such a small amplitude, that while the valve 5 is closing the Working piston 71 through the valve cam 3 still in Area of its top dead center is held, so that Hydraulic medium via overflow connection 73 can drain off.
  • the fuel cam 4 and / or the valve cam 3 must not be configured symmetrically have to.
  • the two flanks 31, 32 of the valve cam 3 can of course also be different, e.g. B. be designed differently steep or long. The the same applies to the flanks of the fuel cam 4.
  • Fig. 5 shows a symbolic representation second embodiment of the invention.
  • the essential difference to the first embodiment relates to the means for closing the valve 5. Otherwise the explanations of the first apply Embodiment in an analogous manner also for the second embodiment.
  • the second Execution example is also one of the Valve cam 3 actuated stroke pump 7 'provided connected to the valve 5 via the hydraulic line 8 is to operate this hydraulically.
  • the means that control the closing of valve 5, include here electrically or electronically controlled valve 20 for Pressure relief of the hydraulic line 8.
  • the electrical or electronically controlled valve 20 can either be directly controlled or piloted.
  • the hydraulic line 8 leads from the stroke pump 7 ' the electromechanical valve 20 and from this to Exhaust valve 5.
  • Symbolic in Fig. 5 shown position of the valve 20 is the Stroke pump 7 'connected to the outlet valve 5, so that the hydraulic medium as soon as it is under sufficient Pressure is present, the outlet valve 5 opens.
  • the valve 20 is in a position brought as symbolically in the right part of the valve 20 is shown, that is, the part of Hydraulic line 8 from the outlet of the valve 20 to Exhaust valve 5 leads to the return duct 10 connected so that the hydraulic medium from said part the hydraulic line 8 controlled by the Return channel 10 can flow. This takes place Pressure relief of the exhaust valve 5 and thus be Conclude.
  • the return channel 10 is either with the Feed line 11 for the hydraulic medium or directly with connected to the reservoir 13 for the hydraulic medium.
  • the valve 20 is actuated by means of a Control pulse from a control unit 60 via the Signal line 50 reaches the valve 20. So that Close the outlet valve 5 to the desired one Time, that is at the desired crank angle KW, a measuring device is provided, which the angular position of the control shaft 2 is detected.
  • the Measuring device includes, for example, an angle encoder 30, via a signal line 40 to the control unit 60 is connected. As soon as the control unit 60 uses the Signal transmitted by the angle encoder 30 recognizes that the exhaust valve 5 must be closed, it generates a control pulse that over the signal line 50 corresponding actuation of the valve 20 triggers.
  • the control unit 60 recognizes that the exhaust valve 5 must be closed.
  • proximity sensors, Position sensors, induction sensors, photodiodes or Similar means can be provided, for example the position of the working piston 71 of the stroke pump 7 ' or the angular position of the valve cam 3 can be detected is.
  • the invention thus an arrangement and a Method for valve control of a reversible Diesel engine provided under apparatus and construction aspects particularly simple and are therefore inexpensive, where the control shaft, the cams and the enclosures enclosing them in particular are compact and space-saving, and that too optimal operating behavior for both Allow forwards and backwards runs.

Description

Die Erfindung betrifft eine Anordnung und ein Verfahren zur Ventilsteuerung einer umsteuerbaren Dieselbrennkraftmaschine gemäss dem Oberbegriff des jeweiligen unabhängigen Patentanspruchs.The invention relates to an arrangement and a method for valve control of a reversible Diesel engine according to the preamble of respective independent claim.

Bei umsteuerbaren Dieselbrennkraftmaschinen, insbesondere Grossdieselmotoren wie sie beispielsweise im Schiffsbau eingesetzt werden, erfolgt die Steuerung der Brennstoffeinspritzung und der Ventile der Zylinder, (Auslass- und/oder Einlassventile), mittels einer Steuerwelle, auf welcher pro Zylinder ein Brennstoffnocken zur Steuerung der Brennstoffeinspritzung sowie für jedes Ventil ein Ventilnocken zur Steuerung dieses Ventils vorgesehen ist. Die Steuerwelle wird dabei von der Kurbelwelle angetrieben und die Brennstoff- bzw. Ventilnocken betätigen ihnen zugeordnete Aktuatoren, z.B. Einspritzpumpen bzw. Hubgeberpumpen, welche der Brennstoffeinspritzung bzw. der hydraulischen Ventilbetätigung dienen. Um für beide Drehrichtungen einer umsteuerbaren Brennkraftmaschine, nämlich Vorwärts- und Rückwärtslauf, gleiche Bedingungen für die Brennstoffeinspritzung und deren Zusammenspiel mit der Ventilbetätigung zu schaffen, sind Massnahmen notwendig, weil im allgemeinen der Winkelversatz zwischen dem Brennstoffnocken und dem Ventilnocken, z. B. für das Auslassventil, auf der Steuerwelle für die beiden Drehrichtungen der Steuerwelle nicht gleich ist, sofern beide Nocken unverrückbar auf der Steuerwelle sitzen.In reversible diesel engines, in particular Large diesel engines such as those used in shipbuilding are used, the control of the Fuel injection and the valves of the cylinders, (Exhaust and / or intake valves), by means of a Control shaft, on which one per cylinder Fuel cams to control fuel injection as well as a valve cam for control for each valve this valve is provided. The tax wave will be there driven by the crankshaft and the fuel or Valve cams actuate actuators assigned to them, e.g. Injection pumps or stroke pumps, which the Fuel injection or hydraulic Serve valve actuation. In order for both directions of rotation a reversible internal combustion engine, namely forward and reverse running, equal conditions for that Fuel injection and its interaction with the To create valve actuation, measures are necessary because in general the angular offset between the Fuel cam and the valve cam, e.g. B. for that Exhaust valve, on the control shaft for the two Direction of rotation of the control shaft is not the same, provided both cams sit immovably on the control shaft.

Sind beispielsweise der Brennstoff- und der Ventilnocken für das Auslassventil so angeordnet, dass beim Vorwärtslauf der Scheitel des Auslassventilnockens dem des Brennstoffnockens um einen Kurbelwinkel von 145° nacheilt, so ergibt sich bei einer Umkehr der Drehrichtung (Rückwärtslauf), dass der Scheitel des Auslassventilnockens dem des Brennstoffnockens um einen Kurbelwinkel von 215° nacheilt, sodass die Abfolge zwischen Brennstoffeinspritzung und Auslassventilbetätigung (bezogen auf den Bewegungszyklus des Kolbens im Zylinder) nicht mehr derjenigen des Vorwärtslaufs entspricht. Dies hat zur Folge, dass das Betriebsverhalten der Brennkraftmaschine beim Rückwärtslauf stark verschlechtert ist.Examples are the fuel and valve cams arranged for the exhaust valve so that the Forward the apex of the exhaust valve cam the fuel cam by a crank angle of 145 ° lags, the reversal results in Direction of rotation (reverse running) that the apex of the Exhaust valve cam that of the fuel cam by one Crank angle lagged by 215 °, so the sequence between fuel injection and Exhaust valve actuation (based on the movement cycle of the piston in the cylinder) no longer that of the Forward running corresponds. As a result, the Operating behavior of the internal combustion engine at Reverse run is badly deteriorated.

In der DE-A-31 28 332 wird deshalb vorgeschlagen, die Brennstoffnocken für den Umsteuerbetrieb bezüglich der Steuerwelle zu verdrehen, das heisst die Brennstoffnocken können bezüglich ihrer Winkelposition auf der Steuerwelle zwischen zwei Positionen umgesteuert werden, während die Auslassventilnocken für beide Drehrichtungen der Steuerwelle in der gleichen Winkelposition bezüglich der Steuerwelle verbleiben. Durch diese Massnahme ist gewährleistet, dass die Steuerzeitpunkte für beide Drehrichtungen optimal sind. Die Umsteuerung der Brennstoffnocken erfolgt dabei mittels hydraulicher Umsteuervorrichtungen, welche die Brennstoffnocken bezüglich der Steuerwelle von der Position für den Vorwärtslauf in die für den Rückwärtslauf verdrehen bzw. umgekehrt. DE-A-31 28 332 therefore proposes that Fuel cams for reversing operation with respect to Twisting the control shaft means the fuel cams can with respect to their angular position on the control shaft can be switched between two positions while the Exhaust valve cams for both directions of rotation of the Control shaft in the same angular position with respect to the Control shaft remain. This measure is ensures that the tax dates for both Rotation directions are optimal. The reversal of the Fuel cams are made by means of hydraulic Reversing devices, the fuel cams with respect to the control shaft from the position for the Twist the forward run into the for the reverse run or vice versa.

Obgleich sich diese Aussgestaltung durchaus als funktionstüchtig bewährt hat, so bringt sie doch einen relativ grossen Aufwand mit sich. Da die Umsteuervorrichtungen jeweils nur zwei Brennstoffnocken verdrehen können, müssen pro Zylinderpaar der Brennkraftmaschine eine solche Umsteuervorrichtung auf der Steuerwelle sowie die jeweils notwendigen Versorgungsleitungen vorgesehen sein. Zudem vergrössern diese Umsteuervorrichtungen den Platzbedarf. Zum einen müssen die Brennstoffnocken und zum anderen die Gehäuse, in denen die Steuerwelle angeordnet sind, z. B. die Brennstoffpumpengehäuse, grösser ausgestaltet werden.Although this design turns out quite well tried and tested, it brings you one relatively great effort. Since the Reversing devices only two fuel cams each must be able to twist the Internal combustion engine such a reversing device the control shaft and the respectively necessary Supply lines may be provided. Also enlarge these reversing devices take up space. On the one hand the fuel cams and the housing, in which the control shaft are arranged, e.g. B. the Fuel pump housing can be made larger.

Ausgehend von diesem Stand der Technik ist es deshalb eine Aufgabe der Erfindung, eine einfache Anordnung zur Ventilsteuerung einer umsteuerbaren Dieselbrennkraftmaschine vorzuschlagen, bei welcher die Steuerwelle bezüglich ihres Umfangs sehr platzsparend ausgestaltet ist, und die für beide Drehrichtungen der Steuerwelle eine im wesentlichen gleiche Ventilsteuerung im Bezug auf die Brennstoffeinspritzung ermöglicht. Die Anordnung soll apparativ und konstruktiv einfach und mit relativ geringem Aufwand realisierbar sein. Ferner ist es eine Aufgabe der Erfindung ein entsprechendes Verfahren zur Ventilsteuerung der Aus- und/oder Einlassventile einer umsteuerbaren Dieselbrennkraftmaschine vorzuschlagen.It is therefore based on this state of the art an object of the invention, a simple arrangement for Valve control of a reversible Propose diesel engine in which the Control shaft very space-saving in terms of its size is designed, and for both directions of rotation Control shaft a substantially the same valve timing in terms of fuel injection. The Arrangement should be simple in terms of equipment and design and with can be realized relatively little effort. Furthermore, it is an object of the invention a corresponding method for valve control of the exhaust and / or intake valves a reversible diesel engine propose.

Die diese Aufgabe in apparativer und verfahrenstechnischer Hinsicht lösenden Gegenstände der Erfindung sind durch die Merkmale der jeweiligen unabhängigen Ansprüche gekennzeichnet.That this task in apparatus and procedurally resolved objects of Invention are characterized by the features of each characterized independent claims.

Erfindungsgemäss steuert also ein Ventilnocken auf der Steuerwelle das öffnen des Ventils, während das Schliessen des Ventils durch Mittel gesteuert wird, die von dem Ventilnocken verschieden sind. Durch diese Massnahme wird pro Drehrichtung nur noch eine der Flanken des Ventilnockens für die Ventilsteuerung benötigt, weil für die Steuerung des Schliessens des Ventils andere Mittel vorgesehen sind als insbesondere die zweite Flanke des Ventilnockens. Somit kann der Ventilnocken so angeordnet und ausgestaltet werden, dass seine eine Flanke das Öffnen des Ventils beim Vorwärtslauf optimal und bezüglich der Brennstoffeinspritzung auf den gewünschten Zeitpunkt steuert, während seine zweite Flanke für diese Funktionen beim Rückwärtslauf verantwortlich ist.According to the invention thus controls a valve cam on the Control shaft opening the valve while the Closing the valve is controlled by means that are different from the valve cam. Through this The measure is only one of the flanks per direction of rotation of the valve cam for valve control because for controlling the closing of the valve others Means are provided as in particular the second flank of the valve cam. Thus the valve cam can do so be arranged and designed so that its a Flank the opening of the valve when running forward optimally and regarding fuel injection to the desired time controls while its second Edge for these functions when running backwards responsible for.

Somit ist es für den Umkehrbetrieb nicht mehr notwendig, die Brennstoffnocken oder die Ventilnocken einzeln umzusteuern. Dies bedeutet einen erheblich geringeren apparativen und konstruktiven Aufwand, ohne dass für eine der beiden Drehrichtungen Zugeständnisse an eine optimale zeitliche Abfolge von Brennstoffeinspritzung und Ventilbetätigung gemacht werden müssen. Da keine Umsteuervorrichtungen für die einzelnen Nocken vonnöten sind, können die einzelnen Nocken jeweils direkt auf der Steuerwelle befestigt und somit kleiner ausgestaltet werden. In der Folge können auch die Gehäuse, welche die zugehörigen Aktuatoren beinhalten, z. B. die Brennstoffpumpengehäuse, kleiner und kompakter ausgestaltet werden.Thus, it is no longer necessary for the reverse operation the fuel cams or the valve cams individually change course. This means a significantly lower one apparatus and design effort without a concessions of the two directions to an optimal time sequence of fuel injection and Valve actuation must be made. Since none Reversing devices for the individual cams are required are, the individual cams can each directly on the Control shaft attached and thus designed smaller become. As a result, the housing, which the associated actuators include, e.g. B. the Fuel pump housing, smaller and more compact be designed.

Die erfindungsgemässe Anordnung bzw. das erfindungsgemässe Verfahren eignen sich insbesondere für Zwei-Takt-Grossdieselmotoren wie sie z. B. im Schiffsbau eingesetzt werden.The arrangement according to the invention or the Methods according to the invention are particularly suitable for Two-stroke large diesel engines such as B. in shipbuilding be used.

Weitere vorteilhafte Massnahmen und bevorzugte Ausgestaltungen der erfindungsgemässen Anordnung bzw. des erfindungsgemässen Verfahrens ergeben sich aus den abhängigen Ansprüchen.Other advantageous measures and preferred Refinements of the arrangement according to the invention or the The inventive method result from the dependent claims.

Im folgenden wird die Erfindung sowohl in Bezug auf die apparativen als auch auf die verfahrenstechnischen Aspekte anhand der Zeichnung und anhand von Ausführungsbeispielen näher erläutert. In der schematischen, nicht massstäblichen Zeichnung, in der gleiche oder von der Funktion her gleichwertige Teile mit den gleichen Bezugszeichen versehen sind, zeigen:

Fig. 1:
die wesentlichen Teile eines ersten Ausführungsbeispiels der erfindungsgemässen Anordnung, teilweise im Schnitt,
Fig. 2:
ein Diagramm zur Verdeutlichung der Anordnung der Nocken und der Funktionsweise der erfindungsgemässen Anordnung bzw. des erfindungsgemässen Verfahrens,
Fig. 3:
eine Schnittdarstellung eines Ventilnockens,
Fig. 4:
eine Schnittdarstellung einer Variante für den Ventilnocken, und
Fig. 5:
eine symbolische Darstellung eines zweiten Ausführungsbeispiels der Erfindung.
In the following, the invention is explained in more detail both with regard to the apparatus and to the procedural aspects using the drawing and using exemplary embodiments. In the schematic drawing, not to scale, in which the same or functionally equivalent parts are provided with the same reference numerals,
Fig. 1:
the essential parts of a first embodiment of the arrangement according to the invention, partly in section,
Fig. 2:
1 shows a diagram to illustrate the arrangement of the cams and the functioning of the arrangement according to the invention and the method according to the invention,
Fig. 3:
2 shows a sectional illustration of a valve cam,
Fig. 4:
a sectional view of a variant for the valve cam, and
Fig. 5:
a symbolic representation of a second embodiment of the invention.

Bei der folgenden Beschreibung der Erfindung wird mit beispielhaftem Charakter auf einen Zwei-Takt-Grossdieselmotor mit Längsspülung, wie er beispielsweise im Schiffsbau eingesetzt wird, Bezug genommen, wobei das Auslassventil eines Zylinders als Beispiel für das zu steuernde Ventil dient. Natürlich eignet sich die Erfindung in sinngemäss gleicher Weise auch zur Ventilsteuerung von Einlassventilen. Da es für das Verständnis der Erfindung ausreichend ist, beschränken sich die Erläuterungen auf nur einen Zylinder bzw. das Auslassventil dieses Zylinders. Mit "Brennstoffnocken" und "Ventilnocken" sind im folgenden diejenigen Nocken gemeint, welche beide diesem Zylinder zugeordnet sind, d. h. der Brennstoffnocken und der Ventilnocken sind dem gleichen Zylinder zugeordnet. Es versteht sich, dass bei mehreren Zylindern für jeden Zylinder ein Brennstoffnocken und ein Ventilnocken in der im folgenden beschriebenen Weise vorgesehen ist.In the following description of the invention exemplary character on a two-stroke large diesel engine with longitudinal rinsing, as it is for example is used in shipbuilding, referred to, the Exhaust valve of a cylinder as an example of that too controlling valve. Of course, that is suitable Invention in an analogous manner also Valve control of intake valves. Since it's for that Understanding of the invention is sufficient to limit the explanations refer to only one cylinder or that Exhaust valve of this cylinder. With "fuel cams" and "valve cams" are those cams below meant, which are both assigned to this cylinder, d. H. the fuel cam and the valve cam are that assigned to the same cylinder. It is understood that at multiple cylinders for each cylinder Fuel cams and a valve cam in the following described manner is provided.

Fig. 1 zeigt eine Darstellung eines ersten Ausführungsbeispiels der erfindungsgemässen Anordnung zur Ventilsteuerung einer umsteuerbaren - nicht näher dargestellten - Dieselbrennkraftmaschine. Die Anordnung ist gesamthaft mit dem Bezugszeichen 1 versehen. Sie umfasst eine gesamthaft umsteuerbare und in zwei Richtungen drehbare Steuerwelle 2, die in an sich bekannter Weise von der Kurbelwelle der Dieselbrennkraftmaschine angetrieben wird und für beide Drehrichtungen jeweils synchron mit der Kurbelwelle läuft. Die Steuerwelle 2 ist gesamthaft bezüglich der Kurbelwelle umsteuerbar, d. h. beim Umschalten vom Vorwärtslauf in den Rückwärtslauf, bzw. umgekehrt, wird die Steuerwelle 2 gesamthaft um einen Umsteuerwinkel bezüglich der Kurbelwelle verdreht und läuft dann wieder synchron mit der Kurbelwelle. Die Phasenlage der Steuerwelle 2 bezüglich der Kurbelwelle ist also für den Vorwärtslauf eine andere als für den Rückwärtslauf. Das Umsteuern der gesamten Steuerwelle ist eine an sich bekannte Massnahme, die daher hier nicht näher erläutert wird. Es ist beispielsweise möglich, innerhalb des Steuerwellenzahnrads einen Umsteuerservomotor vorzusehen, der in sinngemäss gleicher Weise ausgestaltet ist wie die in der DE-A-31 28 332 beschriebene Umsteuervorrichtung für die Brennstoffnocken. Da im Steuerwellenzahnrad genügend Platz vorhanden ist, stellt es kein Problem dar, den Umsteuerservomotor so auszugestalten, dass das von ihm erzeugte Moment zum Umsteuern der gesamten Steuerwelle 2 ausreichend ist.Fig. 1 shows an illustration of a first Embodiment of the inventive arrangement for Valve control of a reversible - not closer illustrated - diesel engine. The order is generally provided with the reference number 1. she includes one completely reversible and in two Directions rotatable control shaft 2, which in itself known manner from the crankshaft Diesel engine is powered and for both The directions of rotation are synchronous with the crankshaft running. The control shaft 2 is overall with respect to Reversible crankshaft, d. H. when switching from Forward run in reverse, or vice versa the control shaft 2 in total by a reversal angle twisted with respect to the crankshaft and then runs again synchronized with the crankshaft. The phase position of the Control shaft 2 with respect to the crankshaft is therefore for the Forward run is different than for reverse run. The Rerouting the entire tax wave is one in itself known measure, which is therefore not explained in detail here becomes. It is possible, for example, within the Control shaft gear to provide a reversing servo motor, which is designed in the same way as that reversing device described in DE-A-31 28 332 for the fuel cams. Because in the timing shaft gear if there’s enough space, it’s not a problem, to design the reversing servo motor in such a way that moment created him to reverse the whole Control shaft 2 is sufficient.

Auf der Steuerwelle 2 ist ein Brennstoffnocken 4 zur Steuerung der Brennstoffeinspritzung in den Brennraum eines nicht dargestellten Zylinders einer Dieselbrennkraftmaschine und ein Ventilnocken 3 zur Steuerung eines Ventils 5, beispielsweise eines Auslassventils 5, des gleichen Zylinders vorgesehen. Der Brennstoffnocken 4 betätigt in an sich bekannter Weise z. B. eine nicht dargestellte Brennstoffeinspritzpumpe, die den Brennstoff zur der Einspritzdüse oder den Einspritzdüsen des Zylinders fördert.A fuel cam 4 is on the control shaft 2 Control of fuel injection into the combustion chamber of a cylinder, not shown Diesel engine and a valve cam 3 for Control of a valve 5, for example one Exhaust valve 5, the same cylinder provided. The Fuel cam 4 actuates in a manner known per se z. B. a fuel injection pump, not shown, which the fuel to the injector or the Injectors of the cylinder promotes.

Der Ventilnocken 3 betätigt über eine Folgerrolle 6 eine Hubgeberpumpe 7, deren Arbeitskolben 71 in einer Buchse 74 geführt ist und einen Arbeitsraum 72 begrenzt. Der Arbeitsraum 72 ist über eine Hydraulikleitung 8 mit dem Auslassventil 5 verbunden, um dieses hydraulisch zu betätigen. Bei einer Kompressionsbewegung des Arbeitskolbens 71 der Hubgeberpumpe 7 - darstellungsgemäss also einer Aufwärtsbewegung - wird ein Hydraulikmedium in der Hydraulikleitung 8 unter Druck gesetzt, wodurch das Auslassventil 5 geöffnet wird. Auf diese Weise steuert der Ventilnocken 3 das Öffnen des Auslassventils 5.The valve cam 3 actuates a follower roller 6 Stroke pump 7, the working piston 71 in a socket 74 is guided and delimits a working space 72. The Working space 72 is connected to the hydraulic line 8 Exhaust valve 5 connected to this hydraulically actuate. With a compression movement of the Working piston 71 of the stroke pump 7 - as shown an upward movement a hydraulic medium in the hydraulic line 8 under pressure set, whereby the exhaust valve 5 is opened. On in this way, the valve cam 3 controls the opening of the Exhaust valve 5.

Erfindungsgemäss sind von dem Ventilnocken 3 verschiedenen Mittel vorgesehen, welche das Schliessen des Ventils 5 steuern. Bei dem ersten Ausführungsbeispiel umfassen diese Mittel eine in der Hubgeberpumpe vorgesehene Überströmverbindung 73 zur Druckentlastung der Hydraulikleitung 8. Die Überströmverbindung führt vom Arbeitsraum 72 der Hubgeberpumpe 7 zu einer Ringnut 75 in der Mantelfläche des Arbeitskolbens 71. In der Buchse 74 ist mindestens eine Bohrung 76 vorgesehen, die in einen Ringkanal 77 mündet, welcher die äussere Wandung der Buchse 74 in Umfangsrichtung umgibt. Der Ringkanal 77 ist mit einem Auslasskanal 78 verbunden, durch welchen das Hydraulikmedium, beispielsweise ein Öl, abströmen kann. Die Ringnut 75 in der Wandung des Arbeitskolbens 71 einerseits und die Bohrung 76 oder die Bohrungen 76 in der Buchse 74 andererseits sind relativ zueinander derart angeordnet, dass sie nur dann miteinander verbunden sind, wenn sich der Arbeitskolben 71 im Bereich seines oberen Totpunkts befindet. Mit oberem Totpunkt ist dabei derjenige Umkehrpunkt des Arbeitskolbens 71 gemeint, bei dem das Volumen des Arbeitsraums 72 minimal ist.According to the invention, valve cam 3 various means are provided which the closing of valve 5 control. In the first embodiment these means include one in the stroke pump provided overflow connection 73 for pressure relief the hydraulic line 8. The overflow connection leads from Working space 72 of the stroke pump 7 to an annular groove 75 in the outer surface of the working piston 71. In the bushing 74 there is at least one bore 76 provided in one Ring channel 77 opens out, which the outer wall of the Surrounds sleeve 74 in the circumferential direction. The ring channel 77 is connected to an outlet duct 78 through which the Hydraulic medium, for example an oil, can flow out. The annular groove 75 in the wall of the working piston 71 on the one hand and the bore 76 or the bores 76 in the socket 74, on the other hand, are such relative to one another arranged that they are only connected to each other if the working piston 71 in the area of its upper Dead center is located. With top dead center is there the reversal point of the working piston 71 is meant at which the volume of the working space 72 is minimal.

Bei dem ersten Ausführungsbeispiel umfassen die Mittel, die das Schliessen des Ventils 5 steuern, ferner eine Drosseleinrichtung, z. B. ein Drosselventil 9, zu welchem der Auslasskanal 78 führt. Das Drosselventil 9 dient der Regelung der Druckentlastung der Hydraulikleitung 8. Von dem Drosselventil 9 erstreckt sich ein Rückführkanal 10, der in eine Zuführleitung 11 für das Hydraulikmedium mündet. Die Zuführleitung 11 führt von einem nicht dargestellten Vorratsbehälter für das Hydraulikmedium über ein Rückschlagventil 12 und mündet in die Hydraulikleitung 8 ein.In the first embodiment, the means include which control the closing of the valve 5, also one Throttle device, e.g. B. a throttle valve 9, to which the outlet duct 78 leads. The throttle valve 9 is used Hydraulic line pressure relief control 8. From the throttle valve 9 extends a return duct 10, the in a supply line 11 for the hydraulic medium empties. The feed line 11 does not lead from one shown reservoir for the hydraulic medium via a check valve 12 and opens into the Hydraulic line 8 a.

Sowohl der Brennstoffnocken 4 als auch der Ventilnocken 3 sind bezüglich der Steuerwelle 2 ortsfest fixiert. Der Ventilnocken 3 ist derart angeordnet und ausgestaltet, dass das Öffnen des Ventils relativ zur Brennstoffeinspritzung um einen Kurbelwinkel versetzt erfolgt, der für beide Drehrichtungen der Steuerwelle 2 im wesentlichen gleich ist. Fig. 3 zeigt in einer Querschnittsdarstellung einen solchen Ventilnocken 3. Die Kontur des Ventilnockens 3 umfasst eine erste Flanke 31 sowie eine zweite Flanke 32. Zwischen den beiden Flanken 31,32 weist der Ventilnocken 3 einen mittleren Bereich 34 auf, in welchem seine Kontur im wesentlichen parallel zum Grundkreis 33 verläuft. Aufgrund dieses mittleren Bereichs weist die Kontur des Ventilnockens 3 zwei effektive Scheitelpunkte S1 und S2 auf, von denen je einer im Übergangsbereich zwischen der ersten Flanke 31 und dem mittleren Bereich 34 und im Übergangsbereich zwischen dem mittleren Bereich 34 und der zweiten Flanke 32 liegt. Mit "effektivem Scheitelpunkt" ist dabei derjenige Punkt der Kontur des Ventilnockens 3 gemeint, auf dem die Folgerrolle 6 (Fig. 1) aufliegt, wenn der Öffnungsvorgang des Ventils 5 gerade abgeschlossen ist, d. h. wenn das Ventil 5 gerade ganz geöffnet ist. Befindet sich die Folgerrolle 6 an einem der effektiven Scheitelpunkte, so ist der Arbeitskolben 71 der Hubgeberpumpe 7 in etwa in seinem oberen Totpunkt.Both the fuel cam 4 and the valve cam 3 are fixed with respect to the control shaft 2. The Valve cam 3 is arranged and designed in such a way that opening the valve relative to the Fuel injection offset by a crank angle takes place for both directions of rotation of the control shaft 2 is essentially the same. Fig. 3 shows in a Cross-sectional view of such a valve cam 3. Die The contour of the valve cam 3 comprises a first flank 31 and a second flank 32. Between the two flanks 31, 32, the valve cam 3 has a central region 34 in which its contour is essentially parallel to Base circle 33 runs. Because of this middle Area has the contour of the valve cam 3 two effective vertices S1 and S2, each of which one in the transition area between the first flank 31 and the middle region 34 and in the transition region between the middle region 34 and the second flank 32 lies. With "effective vertex" is there that point of the contour of the valve cam 3 is meant, on which the follower roller 6 (Fig. 1) rests when the Opening process of valve 5 has just been completed, d. H. when the valve 5 is just fully open. The follower role 6 is on one of the effective ones Vertices, the working piston 71 is the Stroke pump 7 approximately in its top dead center.

Der Ventilnocken 3 ist derart ausgestaltet, dass die beiden effektiven Scheitelpunkte S1,S2 so angeordnet sind, dass - unabhängig von der Drehrichtung - jeweils der in Drehrichtung erste Scheitelpunkt S1 oder S2 relativ zum Scheitelpunkt des Brennstoffnockens 4 um den gleichen Winkel versetzt ist. Dies bedeutet z. B., dass die beiden effektiven Scheitelpunkte S1 und S2 relativ zueinander um einen Winkel versetzt sind, der im wesentlichen gleich dem Umsteuerwinkel ist, oder mit anderen Worten, dass die Länge des mittleren Bereichs 34 im wesentlichen dem Umsteuerwinkel entspricht.The valve cam 3 is designed such that the two effective vertices S1, S2 so arranged are that - regardless of the direction of rotation - each the first vertex S1 or S2 in the direction of rotation relative to the vertex of the fuel cam 4 around the is offset at the same angle. This means e.g. B. that the two effective vertices S1 and S2 relative are offset from each other by an angle which in is essentially equal to the reversal angle, or with in other words, the length of the central region 34 corresponds essentially to the reversal angle.

Die Funktionsweise der Anordnung 1 bzw. des erfindungsgemässen Verfahrens wird im folgenden anhand des Diagramms in Fig. 2 erläutert. Dabei wird mit beispielhaftem Charakter davon ausgegangen, dass die Einspritzung des Brennstoffs spätestens bei einem Kurbelwinkel KW von 35° abgeschlosen sein soll, d. h. bei einem Kurbelwinkel KW von 35° hat der Aktuator der Brennstoffpumpe seinen oberen Totpunkt erreicht. Die Öffnung des Auslassventils 5 soll bei einem Kurbelwinkel KW von 180° erfolgen. Der allgemein üblichen Nomenklatur folgend bezieht sich der Kurbelwinkel KW auf die Stellung des Kolbens im Zylinder der Brennkraftmaschine. Konventionsgemäss ist der Kurbelwinkel KW = 0°, wenn sich der Kolben in seinem oberen Totpunkt befindet und KW = 180°, wenn sich der Kolben in seinem unteren Totpunkt befindet.The operation of the arrangement 1 and the The method according to the invention is described below of the diagram in Fig. 2 explained. Thereby with exemplary character assumed that the Fuel injection at the latest at one Crank angle KW of 35 ° should be completed, d. H. at the actuator has a crank angle KW of 35 ° Fuel pump reaches its top dead center. The Opening of the exhaust valve 5 should be at a crank angle KW of 180 °. The common nomenclature below the crank angle KW refers to the position of the piston in the cylinder of the internal combustion engine. Conventionally, the crank angle KW = 0 ° when the piston is at top dead center and KW = 180 ° when the piston is in its lower Dead center is located.

Das Diagramm in Fig. 2 verdeutlicht die Anordnung der Nocken 3,4 auf der Steuerwelle 2 in einer linearisierten Darstellung. Auf der Achse V sind die Kurbelwinkel KW für Vorwärtslauf eingetragen, auf der Achse R diejenigen für Rückwärtslauf. Der Scheitel des Brennstoffnockens 4 liegt für beide Richtungen bei KW = 35°. Der Umsteuerwinkel, um den die Steuerwelle beim Wechsel der Drehrichtung umgesteuert wird, ist im wesentlichen gleich dem doppelten Winkelabstand des Scheitels des Brennstoffnockens 4 vom oberen Totpunkt des Kolbens (KW = 0°), also in dem konkreten Beispiel 70° (wobei zusätzlich noch eine Reserve vorgesehen sein kann).The diagram in Fig. 2 illustrates the arrangement of the Cam 3,4 on the control shaft 2 in a linearized Presentation. On the axis V are the crank angles KW for Forward run entered, those for the R axis Reverse. The apex of the fuel cam 4 lies for both directions at KW = 35 °. The reversal angle in order the control shaft when changing the direction of rotation is reversed is essentially the same double angular distance of the apex of the Fuel cam 4 from top dead center of the piston (KW = 0 °), i.e. 70 ° in the specific example (with additional a reserve can still be provided).

Der erste effektive Scheitelpunkt S1 des Ventilnockens 3 liegt beim Vorwärtslauf bei KW = 180°, sodass er zum Scheitelpunkt des Brennstoffnockens 4 einen Winkelabstand d1 von 145° KW hat. Der mittlere Bereich 34 des Ventilnockens hat eine Länge d2, die 70° KW, also dem Umsteuerwinkel entspricht. Folglich liegt der zweite effektive Scheitelpunkt S2 für den Vorwärtslauf bei KW = 250°. Sein Winkelabstand d3 zum Brennstoffnocken 4 in Vorwärtslaufrichtung (Achse V) gesehen beträgt somit ebenfalls 145°. The first effective vertex S1 of the valve cam 3 is in the forward run at KW = 180 °, so that it to Vertex of the fuel cam 4 an angular distance has d1 of 145 ° KW. The middle area 34 of the Valve cam has a length d2, the 70 ° KW, that is Reversal angle corresponds. Hence the second effective vertex S2 for the forward run at KW = 250 °. Its angular distance d3 to the fuel cam 4 seen in the forward direction (axis V) is thus also 145 °.

Im Vorwärtslaufbetrieb erfolgt nun zunächst die Brennstoffeinspritzung, die durch den Brennstoffnocken 4 gesteuert wird, dessen Scheitelpunkt bei KW = 35° liegt. Beim weiteren Drehen der Steuerwelle 2 läuft die Folgerrolle 6 (Fig. 1) auf die erste Flanke 31 des Ventilnockens 3 auf, wodurch der Arbeitskolben 71 der Hubgeberpumpe 7 darstellungsgemäss (Fig. 1) nach oben bewegt wird. Mit zunehmender Hubbewegung des Arbeitskolbens 71 steigt der Druck in der Hydraulikleitung 8 und das Öffnen des Ventils 5 beginnt. Wenn die Folgerrolle 6 am ersten Scheitelpunkt S1 angelangt ist (KW = 180°), ist das Auslassventil 5 ganz geöffnet und der Arbeitskolben 71 der Hubgeberpumpe 7 befindet sich im Bereich seines oberen Totpunkts. Dadurch öffnet sich die Verbindung zwischen der Ringnut 75 und der Bohrung 76, sodass das Hydraulikmedium aus dem Arbeitsraum 72 durch die Überströmverbindung 73, die Ringnut 75, die Bohrung 76, den Ringkanal 77 und den Auslasskanal 78 abströmen kann. Folglich fällt der Druck in der Hydraulikleitung 8 ab (Druckentlastung), wodurch das Ventil 5 geschlossen wird. Durch Regeln oder Einstellen des Drosselventils 9 lässt sich dabei der Schliessvorgang bzw. der Schliesszeitpunkt kontrolliert beeinflussen bzw. steuern. Von dem Drosselventil 9 gelangt das abströmende Hydraulikmedium durch den Rückführkanal 10 in die Zuführleitung 11. Das Schliessen des Ventils 5 erfolgt also durch Druckentlastung der Hydraulikleitung 8, wobei während des Schliessens des Ventils 5 der Arbeitskolben 71 der Hubgeberpumpe 7 durch den Ventilnocken 3 im Bereich seines oberen Totpunkts gehalten wird, das heisst die Folgerrolle 6 läuft über den mittleren Bereich 34 des Ventilnockens 3. Nachdem die Folgerrolle 6 über den zweiten Scheitelpunkt S2 hinweg gerollt ist, bewegt sich der Arbeitskolben 71, z. B. aufgrund einer nicht dargestellten, an sich bekannten Federbelastung, darstellungsgemäss (Fig. 1) nach unten, wodurch zum einen die Überströmverbindung 73 verschlossen wird und zum anderen Hydraulikmedium aus der Zuführleitung 11 in die Hydraulikleitung 8 angesaugt wird, sobald der Druck in der Hydraulikleitung 8 so weit abgefallen ist, dass das Rückschlagventil 12 öffnet. Beim weiteren Drehen der Steuerwelle 3 erfolgt dann wieder die Brennstoffeinspritzung gesteuert durch den Brennstoffnocken 4, dessen Scheitel wieder bei KW = 395°, was KW = 35° entspricht, erreicht wird.In forward-running mode, this is done first Fuel injection by the fuel cam 4 is controlled, the apex of which is KW = 35 °. The further rotation of the control shaft 2 runs Follower role 6 (Fig. 1) on the first flank 31 of the Valve cam 3, whereby the working piston 71 of the Stroke pump 7 as shown (Fig. 1) upwards is moved. With increasing stroke movement of the Working piston 71 increases the pressure in the Hydraulic line 8 and the opening of the valve 5 begins. If the follower role 6 at the first vertex S1 has reached (KW = 180 °), the exhaust valve 5 is complete opened and the working piston 71 of the stroke pump 7 is in the area of its top dead center. Thereby opens the connection between the ring groove 75 and the bore 76 so that the hydraulic medium from the Working space 72 through the overflow connection 73, the Ring groove 75, the bore 76, the ring channel 77 and the Outlet channel 78 can flow. As a result, the pressure drops in the hydraulic line 8 from (pressure relief), whereby the valve 5 is closed. By rules or Setting the throttle valve 9 can be the The closing process or the closing time is checked influence or control. From the throttle valve 9 the flowing hydraulic medium passes through the Return channel 10 into the feed line 11. The closing of the valve 5 is done by relieving the pressure Hydraulic line 8, while during the closing of the Valve 5 of the working piston 71 of the stroke pump 7 through the valve cam 3 in the area of its top dead center is held, that is, the follower role 6 overflows the middle region 34 of the valve cam 3. After the Follower role 6 beyond the second vertex S2 is rolled, the working piston 71 moves, for. B. due to a known, not shown Spring load, as shown (Fig. 1) downwards, whereby on the one hand the overflow connection 73 is closed and the other hydraulic medium from the Feed line 11 sucked into the hydraulic line 8 as soon as the pressure in the hydraulic line 8 has dropped that the check valve 12 opens. At the further rotation of the control shaft 3 then takes place again Fuel injection controlled by the Fuel cam 4, the apex again at KW = 395 °, what corresponds to KW = 35 ° is achieved.

Für den Rückwärtslauf (Achse R in Fig. 2) wird zunächst die Steuerwelle 2 gesamthaft um den Umsteuerwinkel, in dem konkreten Beispiel also um 70°, bezüglich der Kurbelwelle verdreht. Folglich wird der Scheitelpunkt des Brennstoffnockens wiederum bei dem Kurbelwinkel KW = 35° erreicht. Beim weiteren Drehen der Steuerwelle 2 läuft die Folgerrolle 6 auf die zweite Flanke 32 des Ventilnockens 3 auf, wodurch - analog wie vorne beschrieben - das Öffnen des Ventils 5 erfolgt. Das Ventil 5 ist vollständig geöffnet, wenn sich die Folgerrolle 6 auf dem zweiten effektiven Scheitelpunkt S2 des Ventilnockens 3 befindet (KW = 180°). Das Schliessen erfolgt sinngemäss gleich wie beim Vorwärtslauf.For the reverse run (axis R in Fig. 2) is first the control shaft 2 in total by the changeover angle, in the concrete example by 70 °, with respect to the Crankshaft twisted. Consequently, the vertex of the Fuel cam in turn at the crank angle KW = 35 ° reached. The further rotation of the control shaft 2 runs the follower role 6 on the second flank 32 of the Valve cam 3, which - analogous to the front described - the opening of the valve 5 takes place. The Valve 5 is fully open when the Follower role 6 at the second effective vertex S2 of valve cam 3 is located (KW = 180 °). The closing is basically the same as for forward running.

Folglich dient die erste Flanke 31 des Ventilnockens 3 beim Vorwärtslauf und die zweite Flanke 32 beim Rückwärtslauf zur Steuerung der Öffnung des Ventils 5 und für beide Drehrichtungen wird das Schliessen des Ventils 5 durch vom Ventilnocken 3 verschiedenen Mittel gesteuert, mit denen die Druckentlastung der Hydraulikleitung 8 erfolgt. Da somit pro Drehrichtung nur eine Flanke 31 oder 32 des Ventilnockens 3 für die Ventilsteuerung benötigt wird, können die beiden Flanken 31,32 auseinandergezogen werden, sodass der Winkelabstand d1 bzw. d2 (Kurbelwinkeldifferenz) des in Drehrichtung vorderen effektiven Scheitelpunkts S1 bzw. S2 zum Scheitelpunkt des Brennstoffnockens 4 unabhängig von der Drehrichtung der Steuerwelle 2 ist. Damit ist sowohl für den Vorwärts- als auch für den Rückwärtslauf der Dieselbrennkraftmaschine ein optimales Betriebsverhalten gewährleistet, insbesondere im Hinblick auf das Zusammenspiel zwischen Brennstoffeinspritzung und Ventilbetätigung.Consequently, the first edge 31 of the valve cam 3 serves when running forward and the second edge 32 when Reverse to control the opening of the valve 5 and the valve closes for both directions of rotation 5 by 3 different means from the valve cam controlled with which the pressure relief of the Hydraulic line 8 takes place. Since only per direction of rotation a flank 31 or 32 of the valve cam 3 for the Valve control is required, the two edges 31,32 are pulled apart so that the angular distance d1 or d2 (crank angle difference) of in the direction of rotation front effective vertex S1 or S2 to Vertex of the fuel cam 4 regardless of the Direction of rotation of the control shaft 2 is. This is for both the forward as well as the reverse run of the Diesel engine an optimal operating behavior guaranteed, especially with regard to the Interaction between fuel injection and Valve actuation.

Fig. 4 zeigt in einer Schnittdarstellung eine Variante für die Ausgestaltung des Ventilnockens 3. Auch bei dieser Variante ist die Kontur des Ventilnockens zwischen den beiden effektiven Scheitelpunkten S1,S2, also im mittleren Bereich 34, vom Grundkreis verschieden, verläuft aber nicht parallel zum Grundkreis 33, sondern weist ein Minimum auf. Durch diese Massnahme kann die Menge Hydraulikmedium, die zum Schliessen des Ventils 5 abströmen muss, reduziert werden. Durch das Minimum wird nämlich der Arbeitskolben 71 (Fig. 1) der Hubgeberpumpe 7 geringfügig - darstellungsgemäss - nach unten bewegt. Diese Bewegung ist jedoch von solch geringer Amplitude, dass während des Schliessens des Ventils 5 der Arbeitskolben 71 durch den Ventilnocken 3 immer noch im Bereich seines oberen Totpunkts gehalten wird, sodass das Hydraulikmedium über die èberströmverbindung 73 abfliessen kann.Fig. 4 shows a variant in a sectional view for the design of the valve cam 3. Also at this variant is the contour of the valve cam between the two effective vertices S1, S2, i.e. in middle area 34, different from the base circle, but does not run parallel to the base circle 33, but has a minimum. This measure can Amount of hydraulic medium required to close valve 5 must flow out, be reduced. By the minimum namely the working piston 71 (FIG. 1) of the stroke pump 7 slightly - as shown - moved down. However, this movement is of such a small amplitude, that while the valve 5 is closing the Working piston 71 through the valve cam 3 still in Area of its top dead center is held, so that Hydraulic medium via overflow connection 73 can drain off.

Es versteht sich, dass der Brennstoffnocken 4 und/oder der Ventilnocken 3 nicht symmetrisch ausgestaltet sein müssen. Die beiden Flanken 31,32 des Ventilnockens 3 können natürlich auch unterschiedlich, z. B. unterschiedlich steil bzw. lang ausgestaltet sein. Das gleiche gilt für die Flanken des Brennstoffnockens 4.It is understood that the fuel cam 4 and / or the valve cam 3 must not be configured symmetrically have to. The two flanks 31, 32 of the valve cam 3 can of course also be different, e.g. B. be designed differently steep or long. The the same applies to the flanks of the fuel cam 4.

Fig. 5 zeigt in einer symbolischen Darstellung ein zweites Ausführungsbeispiel der Erfindung. Der wesentlichen Unterschied zum ersten Ausführungsbeispiel betrifft die Mittel zum Schliessen des Ventils 5. Ansonsten gelten die Erläuterungen des ersten Ausführungsbeispiels in sinngemäss gleicher Weise auch für das zweite Ausführungsbeispiel. Bei dem zweiten Ausführungbeispiel ist ebenfalls eine von dem Ventilnocken 3 betätigte Hubgeberpumpe 7' vorgesehen, die über die Hydraulikleitung 8 mit dem Ventil 5 verbunden ist, um dieses hydraulisch zu betätigen. Die Mittel, die das Schliessen des Ventils 5 steuern, umfassen hier ein elektrisch oder elektronisch gesteuertes Ventil 20 zur Druckentlastung der Hydraulikleitung 8. Das elektrisch oder elektronisch gesteuerte Ventil 20 kann entweder direkt gesteuert oder vorgesteuert sein.Fig. 5 shows a symbolic representation second embodiment of the invention. The essential difference to the first embodiment relates to the means for closing the valve 5. Otherwise the explanations of the first apply Embodiment in an analogous manner also for the second embodiment. The second Execution example is also one of the Valve cam 3 actuated stroke pump 7 'provided connected to the valve 5 via the hydraulic line 8 is to operate this hydraulically. The means that control the closing of valve 5, include here electrically or electronically controlled valve 20 for Pressure relief of the hydraulic line 8. The electrical or electronically controlled valve 20 can either be directly controlled or piloted.

Die Hydraulikleitung 8 führt von der Hubgeberpumpe 7' zu dem elektromechanischen Ventil 20 und von diesem zum Auslassventil 5. In der in Fig. 5 symbolisch dargestellten Stellung des Ventils 20 ist die Hubgeberpumpe 7' mit dem Auslassventil 5 verbunden, sodass das Hydraulikmedium, sobald es unter ausreichendem Druck steht, das Auslassventil 5 öffnet. Zum Schliessen des Auslassventils 5 wird das Ventil 20 in eine Stellung gebracht, wie sie symbolisch im rechten Teil des Ventils 20 dargestellt ist, das heisst der Teil der Hydraulikleitung 8, der vom Ausgang des Ventils 20 zum Auslassventil 5 führt, wird mit dem Rückführkanal 10 verbunden, sodass das Hydraulikmedium aus genanntem Teil der Hydraulikleitung 8 kontrolliert durch den Rückführkanal 10 abströmen kann. Dadurch erfolgt die Druckentlastung des Auslassventils 5 und somit sein Schliessen. Der Rückführkanal 10 ist entweder mit der Zuführleitung 11 für das Hydraulikmedium oder direkt mit dem Vorratsbehälter 13 für das Hydraulikmedium verbunden. Die Betätigung des Ventils 20 erfolgt mittels eines Steuerimpulses, der von einer Steuereinheit 60 über die Signalleitung 50 zu dem Ventil 20 gelangt. Damit das Schliessen des Auslassventils 5 zum gewünschten Zeitpunkt, das heisst bei dem gewünschten Kurbelwinkel KW, erfolgt, ist eine Messeinrichtung vorgesehen, welche die Winkelstellung der Steuerwelle 2 erfasst. Die Messeinrichtung umfasst beispielsweise einen Winkelgeber 30, der über eine Signalleitung 40 mit der Steuereinheit 60 verbunden ist. Sobald die Steuereinheit 60 anhand des vom Winkelgeber 30 übermittelten Signals erkennt, dass das Auslassventil 5 geschlossen werden muss, erzeugt sie einen Steuerimpuls, der über die Signalleitung 50 die entsprechende Betätigung des Ventils 20 auslöst. Auch bei diesem zweiten Ausführungsbeispiel wird somit das Öffnen des Auslassventils 5 von dem Ventilnocken 3 gesteuert, während zum Steuern des Schliessens des Auslassventils 5 das elektrisch oder elektronisch steuerbare Ventil 20 vorgesehen ist. Natürlich können auch andere Messeinrichtungen vorhanden sein, die ein Signal erzeugen, anhand dessen die Steuereinheit 60 erkennt, dass das Schliessen des Auslassventils 5 erfolgen muss. Beispielsweise können Näherungssensoren, Positionssensoren, Induktionssensoren, Fotodioden oder ähnliche Mittel vorgesehen sein, mit denen beispielsweise die Stellung des Arbeitskolbens 71 der Hubgeberpumpe 7' oder die Winkelstellung des Ventilnockens 3 detektierbar ist.The hydraulic line 8 leads from the stroke pump 7 ' the electromechanical valve 20 and from this to Exhaust valve 5. Symbolic in Fig. 5 shown position of the valve 20 is the Stroke pump 7 'connected to the outlet valve 5, so that the hydraulic medium as soon as it is under sufficient Pressure is present, the outlet valve 5 opens. To close of the exhaust valve 5, the valve 20 is in a position brought as symbolically in the right part of the valve 20 is shown, that is, the part of Hydraulic line 8 from the outlet of the valve 20 to Exhaust valve 5 leads to the return duct 10 connected so that the hydraulic medium from said part the hydraulic line 8 controlled by the Return channel 10 can flow. This takes place Pressure relief of the exhaust valve 5 and thus be Conclude. The return channel 10 is either with the Feed line 11 for the hydraulic medium or directly with connected to the reservoir 13 for the hydraulic medium. The valve 20 is actuated by means of a Control pulse from a control unit 60 via the Signal line 50 reaches the valve 20. So that Close the outlet valve 5 to the desired one Time, that is at the desired crank angle KW, a measuring device is provided, which the angular position of the control shaft 2 is detected. The Measuring device includes, for example, an angle encoder 30, via a signal line 40 to the control unit 60 is connected. As soon as the control unit 60 uses the Signal transmitted by the angle encoder 30 recognizes that the exhaust valve 5 must be closed, it generates a control pulse that over the signal line 50 corresponding actuation of the valve 20 triggers. Also at this second embodiment is thus the opening of the exhaust valve 5 controlled by the valve cam 3, while controlling the closing of the exhaust valve 5 the electrically or electronically controllable valve 20 is provided. Of course, others can too Measuring devices should be present that have a signal generate, based on which the control unit 60 recognizes that the exhaust valve 5 must be closed. For example, proximity sensors, Position sensors, induction sensors, photodiodes or Similar means can be provided, for example the position of the working piston 71 of the stroke pump 7 ' or the angular position of the valve cam 3 can be detected is.

Durch die Erfindung wird somit eine Anordnung und ein Verfahren zur Ventilsteuerung einer umsteuerbaren Dieselbrennkraftmaschine bereitgestellt, die unter apparativen und konstruktiven Aspekten besonders einfach und somit kostengünstig sind, bei denen die Steuerwelle, die Nocken und die sie umschliessenden Gehäuse besonders kompakt und platzsparend ausgestaltet sind, und die zudem ein optimales Betriebsverhalten sowohl für den Vorwärtslauf als auch für den Rückwärtslauf ermöglichen. The invention thus an arrangement and a Method for valve control of a reversible Diesel engine provided under apparatus and construction aspects particularly simple and are therefore inexpensive, where the control shaft, the cams and the enclosures enclosing them in particular are compact and space-saving, and that too optimal operating behavior for both Allow forwards and backwards runs.

Die erfindungsgemässe Anordnung und das erfindungsgemässe Verfahren eignen sich insbesondere für umsteuerbare Zwei-Takt-Grossdieselmotoren, wie sie z. B. im Schiffsbau eingesetzt werden.The arrangement according to the invention and the one according to the invention Methods are particularly suitable for reversible two-stroke large diesel engines, as they e.g. B. in shipbuilding be used.

Claims (10)

  1. Arrangement for the valve control of a reversible diesel combustion engine comprising a control shaft (2) which is reversible and rotatable in two directions, and on which are provided at least one fuel cam (4) for the control of the fuel injection and at least one valve cam (3) for the control of a valve (5) of the diesel combustion engine, with the valve cam (3) controlling the opening of the valve cam (3) controlling the opening of the valve (5), characterised in that means different from the valve cam (3) are provided which control the closing of the valve (5).
  2. Arrangement in accordance with claim 1, in which both the fuel cam (4) and the valve cam (3) are mounted so as to be of fixed location with respect to the control shaft (2), with the valve cam (3) being arranged and designed in such a manner that the opening of the valve (5) occurs with a displacement by a crankshaft angle (KW) relative to the fuel injection which is substantially the same for both directions of rotation of the control shaft (2).
  3. Arrangement in accordance with claim 1 or claim 2, with the contour of the valve cam (3) having two effective apex points (S1, S2) which are arranged in such a manner that - independently of the direction of rotation - the first apex point (S1 or S2) of the valve cam (3) in the respective direction of rotation is displaced in each case by the same angle relative to the apex point of the fuel cam (4).
  4. Arrangement in accordance with claim 3, with the effective apex points (S1, S2) of the valve cam (3) being displaced with respect to one another by an angle which is substantially equal to the reversing angle and with the contour of the valve cam (3) being different from the base circle (33) between the two effective apex points (S1, S2).
  5. Arrangement in accordance with one of the preceding claims, with a lifting pump (7) which is actuated by the valve cam being further provided, which is connected via a hydraulic line (8) to the valve (5) in order to hydraulically actuate the latter, and with the means which control the closing of the valve (5) comprising an overflow connection (73) which is provided in the lifting pump (7) for the pressure relief of the hydraulic line (8).
  6. Arrangement in accordance with claim 5, with the means which control the closing of the valve comprising a restrictor device (9) for the regulation of the pressure relief of the hydraulic line (8).
  7. Arrangement in accordance with one of the claims 1 to 4, with a lifting pump (7') which is actuated by the valve cam and which is connected via a hydraulic line (8) to the valve (5) being provided in order to actuate the latter hydraulically, and with the means which control the closing of the valve (5) comprising an electrically or electronically controlled valve (20) for the pressure relief of the hydraulic line (8).
  8. Method for the valve control of a reversible diesel combustion engine in which a control shaft (2) which is rotatable in two directions, and on which are provided at least one fuel cam (4) for the control of the fuel injection and at least one valve cam (3) for the control of a valve (5) of the diesel combustion engine, is rotated in its entirety for the reverse operation, and in which the opening of the valve (5) is controlled by the valve cam (3), characterised in that the closing of the valve (5) is controlled by means which are different from the valve cam (3).
  9. Method in accordance with claim 8 in which the valve (5) is opened hydraulically by means of a lifting pump (7; 7') which is actuated by the valve cam (3) and in which the valve (5) is closed by means of pressure relief with the working piston (71) of the lifting pump (7; 7') being held in the region of its upper dead centre by the valve cam (3) during the closing of the valve (5).
  10. Reversible diesel combustion engine, in particular a two-cycle large diesel engine, characterised in that it comprises an arrangement in accordance with one of the claims 1 to 7.
EP97810766A 1997-10-14 1997-10-14 Arrangement and method for valve driving in a reversible diesel engine Expired - Lifetime EP0909883B1 (en)

Priority Applications (8)

Application Number Priority Date Filing Date Title
EP97810766A EP0909883B1 (en) 1997-10-14 1997-10-14 Arrangement and method for valve driving in a reversible diesel engine
DK97810766T DK0909883T3 (en) 1997-10-14 1997-10-14 Device and method for valve control of a reversible diesel combustion engine
DE59708956T DE59708956D1 (en) 1997-10-14 1997-10-14 Arrangement and method for valve control of a reversible diesel internal combustion engine
TW087101840A TW360739B (en) 1997-10-14 1998-02-11 Arrangement and method for the valve control of a reversible diesel combustion engine
JP10234228A JPH11159314A (en) 1997-10-14 1998-08-20 Structure and method for controlling valve for reversible diesel engine
PL98329104A PL329104A1 (en) 1997-10-14 1998-10-09 Apparatus for and method of controlling operation of diesel engine valves
CNB981213561A CN1247881C (en) 1997-10-14 1998-10-13 Arrangement and method for valve control of reversible diesel combustion engine
KR1019980042753A KR100527820B1 (en) 1997-10-14 1998-10-13 Arrangement and method for the valve control of a reversible diesel combustion engine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP97810766A EP0909883B1 (en) 1997-10-14 1997-10-14 Arrangement and method for valve driving in a reversible diesel engine

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EP0909883A1 EP0909883A1 (en) 1999-04-21
EP0909883B1 true EP0909883B1 (en) 2002-12-11

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JP (1) JPH11159314A (en)
KR (1) KR100527820B1 (en)
CN (1) CN1247881C (en)
DE (1) DE59708956D1 (en)
DK (1) DK0909883T3 (en)
PL (1) PL329104A1 (en)
TW (1) TW360739B (en)

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CN102251895B (en) * 2006-04-12 2013-03-27 曼柴油机和涡轮公司,德国曼柴油机和涡轮欧洲股份公司的联营公司 Crosshead-shaped large uniflow-type dual-stroke diesel engine
JP2008248838A (en) * 2007-03-30 2008-10-16 Man Diesel As Cam driven exhaust valve operation system for large size two cycle diesel engine
US8033954B2 (en) * 2007-04-18 2011-10-11 GM Global Technology Operations LLC Hybrid powertrain with reversing engine and method of control
CN101509404B (en) * 2008-02-15 2011-05-18 蔡学功 Variable valve system
JP5015975B2 (en) * 2009-02-04 2012-09-05 エムエーエヌ・ディーゼル・アンド・ターボ・フィリアル・アフ・エムエーエヌ・ディーゼル・アンド・ターボ・エスイー・ティスクランド Cam-driven exhaust valve actuation system for large two-cycle diesel engines
JP5189069B2 (en) * 2009-12-17 2013-04-24 エムエーエヌ・ディーゼル・アンド・ターボ・フィリアル・アフ・エムエーエヌ・ディーゼル・アンド・ターボ・エスイー・ティスクランド Cam-driven exhaust valve actuation system for large two-cycle diesel engines
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RU2576093C1 (en) * 2014-10-07 2016-02-27 Анатолий Александрович Рыбаков Method of reversing crankshaft of internal combustion engine by reversing starter mechanism and timing valve pneumatic drive system with its charging with gas from compensating pneumatic accumulator
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RU2576696C1 (en) * 2015-02-05 2016-03-10 Анатолий Александрович Рыбаков Method for reversal internal combustion engine with reverse starter mechanism and pneumatic actuator system of two-valve gas distributor with charging of accumulator of system by atmospheric air
RU2594829C1 (en) * 2015-02-05 2016-08-20 Анатолий Александрович Рыбаков Method for reversing internal combustion engine by reversing starter mechanism and pneumatic drive system of two-valve gas distributor, with charging pneumatic accumulator system using gas from compensating pneumatic accumulator
RU2576699C1 (en) * 2015-02-05 2016-03-10 Анатолий Александрович Рыбаков Method for reversal of internal combustion engine with reverse starter mechanism and pneumatic actuator system of two-valve gas distributor with charging of pneumatic accumulator of system with gas from compensation pneumatic accumulator
RU2578934C1 (en) * 2015-02-19 2016-03-27 Анатолий Александрович Рыбаков Method for reversal of internal combustion engine with starter mechanism and pneumatic actuator system of three-valve gas distributor with charging of accumulator of system by atmospheric air
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KR19990037055A (en) 1999-05-25
DE59708956D1 (en) 2003-01-23
JPH11159314A (en) 1999-06-15
CN1247881C (en) 2006-03-29
EP0909883A1 (en) 1999-04-21
DK0909883T3 (en) 2003-01-06
TW360739B (en) 1999-06-11
CN1214408A (en) 1999-04-21
KR100527820B1 (en) 2006-03-23
PL329104A1 (en) 1999-04-26

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