EP0407842B1 - Motorbremse für luftverdichtende Brennkraftmaschinen - Google Patents

Motorbremse für luftverdichtende Brennkraftmaschinen Download PDF

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Publication number
EP0407842B1
EP0407842B1 EP90112529A EP90112529A EP0407842B1 EP 0407842 B1 EP0407842 B1 EP 0407842B1 EP 90112529 A EP90112529 A EP 90112529A EP 90112529 A EP90112529 A EP 90112529A EP 0407842 B1 EP0407842 B1 EP 0407842B1
Authority
EP
European Patent Office
Prior art keywords
engine
piston
engine brake
exhaust
valve
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
EP90112529A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0407842A1 (de
Inventor
Dieter Wittmann
Heribert Dipl.-Ing. Kubis
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.)
MAN Truck and Bus SE
Original Assignee
MAN Nutzfahrzeuge 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 MAN Nutzfahrzeuge AG filed Critical MAN Nutzfahrzeuge AG
Priority to AT90112529T priority Critical patent/ATE98339T1/de
Publication of EP0407842A1 publication Critical patent/EP0407842A1/de
Application granted granted Critical
Publication of EP0407842B1 publication Critical patent/EP0407842B1/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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/06—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for braking
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D9/00—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits
    • F02D9/04—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits concerning exhaust conduits
    • F02D9/06—Exhaust brakes
    • 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

Definitions

  • the invention relates to an engine brake for air-compressing internal combustion engines.
  • engine brakes which consist of a throttle valve in the engine exhaust.
  • This throttle valve blocks the engine exhaust when the engine brake is actuated, so that the air in the engine cylinder and a subsequent exhaust manifold compresses during the exhaust stroke and thus leads to a braking effect.
  • the throttle valve is usually kept smaller in diameter than the exhaust pipe in order to avoid excessive pressure values.
  • valve train In order to increase the braking power of air-compressing internal combustion engines, it is also known according to DE-OS 30 26 529 to provide the valve train with an effective length of a valve train linkage in the sense of an opening movement of an exhaust valve controllable telescopic member.
  • a piston is installed in a valve tappet, which is acted upon by a pump piston of a hydraulic pump unit via a tappet rod and can open the outlet valve outside the regular opening phase in order to blow off compressed air in the compression cycle, as a result of which the compression work supplied to the piston is destroyed.
  • Each piston of the exhaust valves of a multi-cylinder internal combustion engine has its own Pump piston of the hydraulic pump unit combined into one unit connected via a line.
  • the pump pistons are arranged in a star shape around a cam, which rotates synchronously with a camshaft.
  • This cam can advantageously be arranged on the camshaft itself.
  • the cam is shaped so that the exhaust valves open in the compression cycle in order to blow off the compressed air via an exhaust pipe.
  • Such a unit allows the braking power of the engine to be increased compared to the throttling in the exhaust line which is otherwise customary in the course of the exhaust stroke. Nevertheless, even with such an engine brake, one is unable to bring the braking power into the range of the order of magnitude of the engine useful power.
  • an engine brake in 4-stroke internal combustion engines in which a throttle valve is provided in the engine exhaust pipe, which is closed when the engine brake is actuated, so that braking work is performed during the compression stroke.
  • a second valve can be opened in addition to the outlet valve, so that braking work is also to be performed during the compression cycle.
  • the second valve is constantly open so that the dynamic pressure in the cylinder cannot be controlled and the braking work cannot be optimized.
  • the exhaust valve is also opened in the compression stroke. Due to the opening cross-section of 0.5 to 2 cm2 per 100 liters of volume displaced by the working piston in braking operation, no optimal pressure build-up is achieved in the working cylinder.
  • the braking work resulting from the p-V diagram during the compression stroke does not correspond to the achievable maximum, especially since no information about the opening time of the exhaust valve during the compression stroke is made that is definitely coordinated with the opening cross section.
  • GB-A-21 62 580 it is proposed to close the engine exhaust pipe by means of a throttle valve and synchronously in braking operation to keep the outlet valve open by a certain amount by a hydraulically operated additional device. Due to this constant opening of the exhaust valve, braking work is performed not only in the exhaust stroke but also in the compression stroke. A constant opening of the exhaust valve can not lead to an optimization of the braking work during the compression stroke.
  • the object of the invention is to increase the engine braking power by increasing the braking power during the compression stroke so that the braking power penetrates into the useful power range of the internal combustion engine.
  • an exhaust valve 1 is not only actuated by a cam drive 2, but can also be moved by a piston 3.
  • This piston 3 is acted on by a line 4 from a hydraulic pump unit 5 with hydraulic fluid, with each piston 3 of the outlet valve 1 of a multi-cylinder internal combustion engine in the hydraulic pump unit 5 each having a pump piston 6, which can be raised by a cam 7 such that the outlet valve can be raised by the piston 3, as shown in the operating phase shown.
  • the compressed air throttled through the exhaust valve 1 into an engine exhaust pipe 8 (FIG. 2) can be blown off during a compression stroke and the back expansion work can be destroyed by the control times selected according to the invention.
  • this type of engine brake is combined with a generally known engine brake according to FIG. 2, in which the engine exhaust pipe 8 is partially blocked by a throttle valve 12 when the engine brake is actuated.
  • the throttle valve 12 is adjusted by means of an adjustment mechanism 10, which in the exemplary embodiment shown is designed as a pneumatic piston-cylinder unit 11.
  • the hydraulic pump unit 5 is simultaneously activated by actuating the engine brake, by using compressed air from a vehicle brake system via a pressure line 11 branching into a first and second line 11a, 11b of both the piston-cylinder unit and a control valve (not shown) 10 and the hydraulic pump unit 5 is supplied.
  • braking work is carried out both in the compression stroke and in the extension stroke.
  • the throttle valve 12 in the engine exhaust pipe 8 is being closed, the exhaust valve 1 is opened by the piston 3 via the pump piston 6 during the compression stroke and the compressed air is throttled through the exhaust valve 1 into the engine exhaust pipe 8 which is closed by the throttle valve 12, whereby the back expansion work is destroyed.
  • the throttle valve 12 is designed with a slightly smaller diameter than the engine exhaust pipe, so that an annular gap remains through which a part of the compressed air can escape. The reaction of the compressed air to the pistons of other cylinders, the exhaust valves of which are currently in the open position and which then contribute to the braking power, is particularly advantageous.
  • FIG. 3 shows a control diagram of the piston, intake and exhaust valve, in which the opening stroke of the valves or the piston travel is plotted as a function over the crank angle.
  • the exhaust valve in a first opening phase is somewhat more than 180 °, preferably 220 ° before an ignition dead center in the first point 13 opens and closes at point 14 shortly after ignition dead center.
  • the stroke of the exhaust valve in this opening phase is approximately 1 to 2.5 mm.
  • the compressed air is throttled out through the only partially opened outlet valve 1 (FIG. 1) against an excess pressure of approx. 5 to 6 bar, which builds up when the throttle valve 12 closes. By pushing the air out in the compression cycle, the back expansion work is destroyed.
  • a particular advantage of these control times is that there is only a slight load on an engine valve train and the hydraulic outlet valve actuation at the maximum braking power, since the final compression pressure is greatly reduced.
  • FIG. 4 The braking work performed when the engine brake is actuated is shown in a pressure piston travel diagram in FIG. 4. Beginning in point 17, the air is first pushed out against the pressure building up in the engine exhaust pipe 8 (FIG. 2) following a curve 19 until point 18 reaches top dead center. In a subsequent expansion cycle, the pressure drops following a second curve 20 until the bottom dead center is reached again in point 17.
  • the extension stroke follows, the pressure curve starting at point 17 following a third curve 21 until top dead center is reached again and after opening an intake valve the pressure drops to a pressure prevailing in the intake system.
  • a braking work performed in the first opening phase of the exhaust valve is represented by the area A1 hatched perpendicular to the abscissa and the braking work performed in the second opening phase of the exhaust valve is represented by the obliquely hatched area A2.
  • the braking power is increased by approx. 80 to 90% and compared to an engine brake according to DE-OS 30 26 529, a braking performance increased by approx Effective performance achieved.
  • the engine brake according to the invention can also be actuated in a graduated manner if only the hydraulic pump unit 5 or the throttle valve 12 (FIG. 2) is actuated separately from one another.
  • a particular advantage of the engine brake according to the invention is the full utilization of the mechanical strength of the piston and crank mechanism and the engine cooling system in the braking mode.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Valve Device For Special Equipments (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
EP90112529A 1989-07-12 1990-06-30 Motorbremse für luftverdichtende Brennkraftmaschinen Expired - Lifetime EP0407842B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT90112529T ATE98339T1 (de) 1989-07-12 1990-06-30 Motorbremse fuer luftverdichtende brennkraftmaschinen.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3922884 1989-07-12
DE3922884A DE3922884A1 (de) 1989-07-12 1989-07-12 Motorbremse fuer luftverdichtende brennkraftmaschinen

Publications (2)

Publication Number Publication Date
EP0407842A1 EP0407842A1 (de) 1991-01-16
EP0407842B1 true EP0407842B1 (de) 1993-12-08

Family

ID=6384798

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90112529A Expired - Lifetime EP0407842B1 (de) 1989-07-12 1990-06-30 Motorbremse für luftverdichtende Brennkraftmaschinen

Country Status (8)

Country Link
US (1) US5150678A (enrdf_load_stackoverflow)
EP (1) EP0407842B1 (enrdf_load_stackoverflow)
JP (1) JPH03130511A (enrdf_load_stackoverflow)
AT (1) ATE98339T1 (enrdf_load_stackoverflow)
DD (1) DD298439A5 (enrdf_load_stackoverflow)
DE (2) DE3922884A1 (enrdf_load_stackoverflow)
RU (1) RU2011854C1 (enrdf_load_stackoverflow)
ZA (1) ZA905415B (enrdf_load_stackoverflow)

Families Citing this family (32)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0533684A (ja) * 1991-03-08 1993-02-09 Hino Motors Ltd 排気ブレーキ用バルブの制御方法及び装置
DE4136286A1 (de) * 1991-11-04 1993-05-06 Mannesmann Rexroth Gmbh, 8770 Lohr, De Hydraulischer antrieb fuer die bewegungssteuerung eines stellgliedes, insbesondere fuer eine inkremental variable nockenwellenverstellung
DE4209775A1 (de) * 1992-03-26 1993-09-30 Man Nutzfahrzeuge Ag Vorrichtung zur Steuerung eines Auslaßventils im Motor-Bremsbetrieb
DE59303199D1 (de) * 1993-01-25 1996-08-14 Steyr Nutzfahrzeuge Motorbremse bei einer 4-Takt-Brennkraftmaschine eines Nutzfahrzeuges
DE4309860C1 (de) * 1993-03-26 1994-06-09 Daimler Benz Ag Vorrichtung zur Steuerung von in einem Zylinder einer Brennkraftmaschine komprimierter Luft
DE4334006C2 (de) * 1993-10-06 1996-10-10 Man Nutzfahrzeuge Ag Vorrichtung zur Erhöhung der Motorbremsleistung einer Brennkraftmaschine
WO1995030086A1 (fr) * 1994-04-28 1995-11-09 Nissan Diesel Motor Co., Ltd. Unite de commande de frein sur echappement d'un moteur a gaz
US5647318A (en) 1994-07-29 1997-07-15 Caterpillar Inc. Engine compression braking apparatus and method
US5540201A (en) 1994-07-29 1996-07-30 Caterpillar Inc. Engine compression braking apparatus and method
US5526784A (en) 1994-08-04 1996-06-18 Caterpillar Inc. Simultaneous exhaust valve opening braking system
EP0736672B1 (de) * 1995-04-04 1998-04-08 Steyr Nutzfahrzeuge Ag Verfahren zur Motorbremsung mit einem 4-Takt-Verbrennungsmotor
US5724939A (en) * 1996-09-05 1998-03-10 Caterpillar Inc. Exhaust pulse boosted engine compression braking method
DE19746428A1 (de) * 1997-10-21 1999-04-22 Mannesmann Rexroth Ag Druckerzeugungssystem
US6000374A (en) * 1997-12-23 1999-12-14 Diesel Engine Retarders, Inc. Multi-cycle, engine braking with positive power valve actuation control system and process for using the same
US6085721A (en) * 1998-04-03 2000-07-11 Diesel Engine Retarders, Inc. Bar engine brake
DE19852552C2 (de) * 1998-11-13 2000-10-05 Daimler Chrysler Ag Verfahren zum Betrieb eines im Viertakt arbeitenden Verbrennungsmotors
RU2187660C2 (ru) * 2000-04-10 2002-08-20 Военный автомобильный институт Моторный замедлитель грузовых автомобилей
RU2186994C2 (ru) * 2000-08-15 2002-08-10 Военный автомобильный институт Моторный замедлитель для двигателя внутреннего сгорания
US6609495B1 (en) 2000-12-19 2003-08-26 Caterpillar Inc Electronic control of engine braking cycle
KR100760439B1 (ko) * 2001-08-28 2007-09-20 두산인프라코어 주식회사 2중 슬리브 구조를 가진 타펫에 의한 엔진 브레이크 장치
RU2289709C2 (ru) * 2002-09-27 2006-12-20 Рязанский военный автомобильный институт им. генерала армии В.П. Дубинина Двигатель внутреннего сгорания транспортного средства
DE10350925A1 (de) 2003-10-31 2005-06-02 Daimlerchrysler Ag Motorbremse für einen Verbrennungsmotor
DE102004057574A1 (de) * 2004-11-30 2006-06-08 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Variabler Ventiltrieb einer Brennkraftmaschine
DE102007061420B4 (de) * 2007-12-20 2009-11-26 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Vorrichtung zur Drucklufterzeugung für ein Fahrzeug und Verfahren zum Betreiben einer Vorrichtung zur Drucklufterzeugung
DE102008032774A1 (de) * 2008-07-11 2010-01-14 Man Nutzfahrzeuge Ag Motorbremseinrichtung und Verfahren zur Motorbremsung mit einer Ventil-Zusatzsteuereinheit
AT510237B1 (de) 2010-07-26 2015-12-15 MAN Truck & Bus Österreich AG Verfahren zur motorbremsung
AT510236B1 (de) 2010-07-26 2015-12-15 MAN Truck & Bus Österreich AG Verfahren zur motorbremsung
DE102013019183A1 (de) 2013-11-18 2015-05-21 Man Truck & Bus Ag Verfahren zum Steuern der Motorbremswirkung einer ventilgesteuerten Brennkraftrnaschine
AT516513B1 (de) 2014-12-15 2016-06-15 MAN Truck & Bus Österreich AG Motorbremsvorrichtung für eine Brennkraftmaschine sowie Verfahren zum Betreiben einer Motorbremsvorrichtung
AT516542B1 (de) * 2014-12-15 2019-12-15 Man Truck & Bus Oesterreich Ag Verfahren zum Steuern einer Motorbremsvorrichtung sowie Motorbremsvorrichtung
AT516149B1 (de) * 2014-12-15 2016-03-15 MAN Truck & Bus Österreich AG Verfahren zum Steuern einer Motorbremsvorrichtung sowie Motorbremsvorrichtung
DE102017120150A1 (de) 2017-09-01 2019-03-07 Man Truck & Bus Ag Verfahren zum Bremsen einer Brennkraftmaschine

Family Cites Families (11)

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Publication number Priority date Publication date Assignee Title
GB737353A (en) * 1952-09-24 1955-09-21 Saurer Ag Adolph Improvements in the braking of motor vehicles with four-stroke reciprocating internal combustion engines
DE2832526A1 (de) * 1978-07-25 1980-02-07 Maschf Augsburg Nuernberg Ag Viertakt-brennkraftmaschine mit motor-auspuffbremse
US4333430A (en) * 1979-06-15 1982-06-08 Rosquist Von D Engine brake
DE3026529A1 (de) * 1980-07-12 1982-02-11 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8500 Nürnberg Motorbremse fuer eine verbrennungskraftmaschine
JPS57171011A (en) * 1981-04-13 1982-10-21 Mitsubishi Motors Corp Braking device for multicylinder four stroke cycle internal combustion engine
US4510900A (en) * 1982-12-09 1985-04-16 The Jacobs Manufacturing Company Hydraulic pulse engine retarder
DE3428627A1 (de) * 1984-08-03 1986-02-13 Daimler-Benz Ag, 7000 Stuttgart Viertakt-brennkraftmaschine
DE3428626A1 (de) * 1984-08-03 1986-02-13 Daimler-Benz Ag, 7000 Stuttgart Viertakt-brennkraftmaschine
US4592319A (en) * 1985-08-09 1986-06-03 The Jacobs Manufacturing Company Engine retarding method and apparatus
DE3712020A1 (de) * 1987-04-09 1988-10-27 Schaeffler Waelzlager Kg Ventilsteuereinrichtung
EP0320536A1 (en) * 1987-12-15 1989-06-21 Van Doorne's Bedrijfswagenfabriek DAF B.V. Engine compression brake

Also Published As

Publication number Publication date
DE3922884A1 (de) 1991-01-24
JPH03130511A (ja) 1991-06-04
DE59003764D1 (de) 1994-01-20
US5150678A (en) 1992-09-29
EP0407842A1 (de) 1991-01-16
RU2011854C1 (ru) 1994-04-30
DE3922884C2 (enrdf_load_stackoverflow) 1992-05-07
ZA905415B (en) 1991-04-24
ATE98339T1 (de) 1993-12-15
DD298439A5 (de) 1992-02-20

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