EP0909883B1 - Anordnung und Verfahren zur Ventilsteuerung einer umsteuerbaren Dieselbrennkraftmaschine - Google Patents

Anordnung und Verfahren zur Ventilsteuerung einer umsteuerbaren Dieselbrennkraftmaschine 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
Authority
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
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0909883A1 (de
Inventor
Wolfgang Stadlin
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Wartsila NSD Schweiz AG
Original Assignee
Wartsila NSD Schweiz AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Wartsila NSD Schweiz AG filed Critical Wartsila NSD Schweiz AG
Priority to EP97810766A priority Critical patent/EP0909883B1/de
Priority to DK97810766T priority patent/DK0909883T3/da
Priority to DE59708956T priority patent/DE59708956D1/de
Priority to TW087101840A priority patent/TW360739B/zh
Priority to JP10234228A priority patent/JPH11159314A/ja
Priority to PL98329104A priority patent/PL329104A1/xx
Priority to CNB981213561A priority patent/CN1247881C/zh
Priority to KR1019980042753A priority patent/KR100527820B1/ko
Publication of EP0909883A1 publication Critical patent/EP0909883A1/de
Application granted granted Critical
Publication of EP0909883B1 publication Critical patent/EP0909883B1/de
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
    • F02F2007/0097—Casings, e.g. crankcases 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.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
EP97810766A 1997-10-14 1997-10-14 Anordnung und Verfahren zur Ventilsteuerung einer umsteuerbaren Dieselbrennkraftmaschine Expired - Lifetime EP0909883B1 (de)

Priority Applications (8)

Application Number Priority Date Filing Date Title
EP97810766A EP0909883B1 (de) 1997-10-14 1997-10-14 Anordnung und Verfahren zur Ventilsteuerung einer umsteuerbaren Dieselbrennkraftmaschine
DK97810766T DK0909883T3 (da) 1997-10-14 1997-10-14 Anordning og fremgangsmåde til ventilstyring af en reverserbar dieselforbrændingskraftmaskine
DE59708956T DE59708956D1 (de) 1997-10-14 1997-10-14 Anordnung und Verfahren zur Ventilsteuerung einer umsteuerbaren Dieselbrennkraftmaschine
TW087101840A TW360739B (en) 1997-10-14 1998-02-11 Arrangement and method for the valve control of a reversible diesel combustion engine
JP10234228A JPH11159314A (ja) 1997-10-14 1998-08-20 可逆ディーゼルエンジンのバルブ制御のための構成及び方法
PL98329104A PL329104A1 (en) 1997-10-14 1998-10-09 Apparatus for and method of controlling operation of diesel engine valves
CNB981213561A CN1247881C (zh) 1997-10-14 1998-10-13 可反转柴油内燃机中用于阀控制的装置和方法
KR1019980042753A KR100527820B1 (ko) 1997-10-14 1998-10-13 가역식디젤연소기관의밸브제어용장치및그방법

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP97810766A EP0909883B1 (de) 1997-10-14 1997-10-14 Anordnung und Verfahren zur Ventilsteuerung einer umsteuerbaren Dieselbrennkraftmaschine

Publications (2)

Publication Number Publication Date
EP0909883A1 EP0909883A1 (de) 1999-04-21
EP0909883B1 true EP0909883B1 (de) 2002-12-11

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP97810766A Expired - Lifetime EP0909883B1 (de) 1997-10-14 1997-10-14 Anordnung und Verfahren zur Ventilsteuerung einer umsteuerbaren Dieselbrennkraftmaschine

Country Status (8)

Country Link
EP (1) EP0909883B1 (da)
JP (1) JPH11159314A (da)
KR (1) KR100527820B1 (da)
CN (1) CN1247881C (da)
DE (1) DE59708956D1 (da)
DK (1) DK0909883T3 (da)
PL (1) PL329104A1 (da)
TW (1) TW360739B (da)

Families Citing this family (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DK0909883T3 (da) * 1997-10-14 2003-01-06 Waertsilae Nsd Schweiz Ag Anordning og fremgangsmåde til ventilstyring af en reverserbar dieselforbrændingskraftmaskine
DE10155669A1 (de) 2001-11-13 2003-05-22 Bosch Gmbh Robert Vorrichtung zur Steuerung mindestens eines Gaswechselventils
CN102251895B (zh) * 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 十字头型的大型单流式双冲程柴油发动机
ATE444442T1 (de) 2006-04-12 2009-10-15 Man B & W Diesel As Grosser zweitakt-kreuzkopf-dieselmotor vom gleichstromtyp
JP2008248838A (ja) * 2007-03-30 2008-10-16 Man Diesel As 大型２サイクルディーゼルエンジン用のカム駆動排気弁作動システム
US8033954B2 (en) * 2007-04-18 2011-10-11 GM Global Technology Operations LLC Hybrid powertrain with reversing engine and method of control
CN101509404B (zh) * 2008-02-15 2011-05-18 蔡学功 可变气门系统
JP5015975B2 (ja) * 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 大型２サイクルディーゼルエンジン用のカム駆動排気弁作動システム
JP5189069B2 (ja) * 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 大型２サイクルディーゼルエンジン用のカム駆動排気弁作動システム
RU2544117C1 (ru) * 2013-12-16 2015-03-10 Анатолий Александрович Рыбаков Способ реверсирования вращения вала двигателя
RU2544121C1 (ru) * 2013-12-16 2015-03-10 Анатолий Александрович Рыбаков Способ реверсирования вращения вала двигателя
RU2543907C1 (ru) * 2013-12-16 2015-03-10 Анатолий Александрович Рыбаков Способ реверсирования вращения вала двигателя
RU2536651C1 (ru) * 2013-12-16 2014-12-27 Анатолий Александрович Рыбаков Способ реверсирования двигателя внутреннего сгорания реверсивным стартером и механизмом привода газораспределительного клапана и топливной форсунки с зарядкой его пневмоаккумулятора сжатым воздухом
RU2538429C1 (ru) * 2014-01-09 2015-01-10 Анатолий Александрович Рыбаков Способ реверсирования вращения коленчатого вала однотактного двигателя с внешней камерой сгорания
RU2566860C1 (ru) * 2014-10-07 2015-10-27 Анатолий Александрович Рыбаков Способ реверсирования вращения коленчатого вала двигателя внутреннего сгорания системой пневматического привода газораспределительного клапана с зарядкой пневмоаккумулятора системы газом из компенсационного пневмоаккумулятора и системой управления топливной форсункой
RU2576093C1 (ru) * 2014-10-07 2016-02-27 Анатолий Александрович Рыбаков Способ реверсирования вращения коленчатого вала двигателя внутреннего сгорания реверсивным стартерным механизмом и системой пневматического привода газораспределительного клапана с зарядкой пневмоаккумулятора системы газом из компенсационного пневмоаккумулятора
RU2576771C1 (ru) * 2015-01-29 2016-03-10 Анатолий Александрович Рыбаков Способ реверсирования двигателя внутреннего сгорания реверсивным стартерным механизмом и системой пневматического привода трёхклапанного газораспределителя с зарядкой пневмоаккумулятора системы воздухом из атмосферы
RU2576700C1 (ru) * 2015-01-29 2016-03-10 Анатолий Александрович Рыбаков Способ реверсирования двигателя внутреннего сгорания реверсивным стартерным механизмом и системой пневматического привода трёхклапанного газораспределителя с зарядкой пневмоаккумулятора системы из компенсационного пневмоаккумулятора
RU2576696C1 (ru) * 2015-02-05 2016-03-10 Анатолий Александрович Рыбаков Способ реверсирования двигателя внутреннего сгорания реверсивным стартерным механизмом и системой пневматического привода двухклапанного газораспределителя с зарядкой пневмоаккумулятора системы воздухом из атмосферы
RU2576699C1 (ru) * 2015-02-05 2016-03-10 Анатолий Александрович Рыбаков Способ реверсирования двигателя внутреннего сгорания стартерным механизмом и системой пневматического привода двухклапанного газораспределителя с зарядкой пневмоаккумулятора системы газом из компенсационного пневмоаккумулятора
RU2594829C1 (ru) * 2015-02-05 2016-08-20 Анатолий Александрович Рыбаков Способ реверсирования двигателя внутреннего сгорания реверсивным стартерным механизмом и системой пневматического привода двухклапанного газораспределителя с зарядкой пневмоаккумулятора системы газом из компенсационного пневмоаккумулятора
RU2578934C1 (ru) * 2015-02-19 2016-03-27 Анатолий Александрович Рыбаков Способ реверсирования двигателя внутреннего сгорания стартерным механизмом и системой пневматического привода трёхклапанного газораспределителя с зарядкой пневмоаккумулятора системы воздухом из атмосферы
RU2581968C1 (ru) * 2015-02-19 2016-04-20 Анатолий Александрович Рыбаков Способ реверсирования двигателя внутреннего сгорания стартерным механизмом и системой пневматического привода трёхклапанного газораспределителя с зарядкой пневмоаккумулятора системы газом из компенсационного пневмоаккумулятора
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KR19990037055A (ko) 1999-05-25
TW360739B (en) 1999-06-11
EP0909883A1 (de) 1999-04-21
DE59708956D1 (de) 2003-01-23
KR100527820B1 (ko) 2006-03-23
CN1247881C (zh) 2006-03-29
JPH11159314A (ja) 1999-06-15
CN1214408A (zh) 1999-04-21
PL329104A1 (en) 1999-04-26

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