EP2143895A1 - Dispositif de frein moteur et procédé de freinage moteur doté d'une unité de commande supplémentaire à soupape - Google Patents

Dispositif de frein moteur et procédé de freinage moteur doté d'une unité de commande supplémentaire à soupape Download PDF

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Publication number
EP2143895A1
EP2143895A1 EP09007579A EP09007579A EP2143895A1 EP 2143895 A1 EP2143895 A1 EP 2143895A1 EP 09007579 A EP09007579 A EP 09007579A EP 09007579 A EP09007579 A EP 09007579A EP 2143895 A1 EP2143895 A1 EP 2143895A1
Authority
EP
European Patent Office
Prior art keywords
valve
additional
control unit
exhaust
oil circuit
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.)
Granted
Application number
EP09007579A
Other languages
German (de)
English (en)
Other versions
EP2143895B1 (fr
Inventor
Werner Kaufhold
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
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Publication date
Application filed by MAN Nutzfahrzeuge AG filed Critical MAN Nutzfahrzeuge AG
Publication of EP2143895A1 publication Critical patent/EP2143895A1/fr
Application granted granted Critical
Publication of EP2143895B1 publication Critical patent/EP2143895B1/fr
Active 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
    • 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
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/18—Rocking arms or levers
    • F01L1/181—Centre pivot rocking arms
    • 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
    • F01L1/20—Adjusting or compensating clearance
    • F01L1/205—Adjusting or compensating clearance by means of shims or the like
    • 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
    • F01L2810/00—Arrangements solving specific problems in relation with valve gears
    • F01L2810/02—Lubrication
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/01—Internal exhaust gas recirculation, i.e. wherein the residual exhaust gases are trapped in the cylinder or pushed back from the intake or the exhaust manifold into the combustion chamber without the use of additional passages

Definitions

  • the invention relates to an engine brake device of a self-igniting 4-stroke reciprocating internal combustion engine, which can be supplied with combustion air by means of at least one intake valve and exhaust gas can be discharged into an exhaust duct by means of at least one exhaust valve, wherein a controllable throttle element is provided in the exhaust duct, the exhaust valve is transferable to an intermediate opened position by means of the throttle element placed in a throttle position, the exhaust valve is connected to a camshaft by means of a mechanical linkage mechanism comprising a hydraulic auxiliary valve control unit and the auxiliary hydraulic control unit holds the exhaust valve in the intermediate opened position.
  • the invention relates to a method for engine braking a self-igniting 4-stroke reciprocating internal combustion engine, which is supplied by at least one inlet valve combustion air and from which by means of at least one exhaust valve exhaust gas is discharged into an exhaust passage, wherein provided in the exhaust passage throttle element for Initiation of engine braking is brought into a throttle position by means of a control, whereby the exhaust gas accumulates in a region between the throttle element and the exhaust valve and a back pressure is built up, whereupon the exhaust valve moves to an intermediate open position, in which intermediate position the exhaust valve by means of a hydraulic valve Additional control unit, which is integrated in a the exhaust valve with a camshaft connecting mechanical link mechanism is held.
  • the additional hydraulic valve control unit is in the variant according to the EP 0 736 672 B1 in a rocker arm of the link mechanism and in the variant according to the EP 1 526 257 A2 mounted on one side in a two outlet valves simultaneously actuated valve bridge of the connection mechanism.
  • An object of the invention is to provide an engine braking device of the type described, which has both a good engine braking effect and a fired engine operation with high exhaust gas recirculation rates allowed.
  • an engine braking device according to the features of claim 1 is given.
  • the additional hydraulic control unit is switched on and off by means of an additional oil circuit provided in addition to a main oil circuit of the internal combustion engine.
  • the additional valve control unit is thus not connected in particular to the main oil circuit of the internal combustion engine, but exclusively to the additional oil circuit.
  • This additional oil circuit in particular its oil pressure, can be adjusted easily and especially without interfering with the areas and components of the internal combustion engine fed by the main oil circuit, selectively and separately adapted to the mode of operation and the operating state of the engine brake device.
  • the additional valve control unit and thus the engine braking device can be activated and deactivated altogether by means of the additional oil circuit. The connection and disconnection can be done in particular synchronously with the operation of the throttle element.
  • the additional valve control unit of the engine brake device is then switched on only by means of the oil pressure of the additional oil circuit set accordingly, if an engine braking effect is actually desired.
  • the auxiliary valve control unit of the engine brake device is deactivated, whereby the undesired opening of the intermediate-opened exhaust valve in this operating situation does not occur. With a correspondingly harder design of the valve spring, even intermediate opening can be prevented.
  • the engine braking device according to the invention equally allows a good engine braking effect if required and otherwise an undisturbed engine operation, which can be used in particular also with high exhaust gas recirculation rates and correspondingly high dynamic pressure values in the exhaust duct.
  • the additional oil circuit may be filled with suitable components, e.g. Pressure reducing valves or booster means in the form of an additional oil pump, be equipped.
  • the additional oil circuit is connected by means of a particular already existing stop on the additional valve control unit. This is very space saving. For the supply of the additional valve control unit with the oil of the additional oil circuit then at least in the area close to the valve practically no additional space is required.
  • an oil feed channel is preferably integrated with a check valve in the stop.
  • the integrated in the connecting mechanism additional valve control unit is preferably designed as a particular check valve-free hydraulic piston-cylinder unit with a reset spring. This relieves the connection mechanism mechanically controlling the movement of the exhaust valve. The number of components to be incorporated into the link mechanism is reduced in this way.
  • Another object of the invention is to provide a method of engine braking according to the type described above, which has both a good engine braking effect and also allows a fired engine operation with high exhaust gas recirculation rates.
  • the additional hydraulic valve control unit can be switched on and off by means of an additional oil circuit provided in addition to a main oil circuit of the internal combustion engine.
  • Fig. 1 is an example of a system diagram of a four-cylinder internal combustion engine 1, which includes a particular intended for lubrication main oil circuit 2 and an additional oil circuit 3 shown.
  • the main oil circuit 2 and the additional oil circuit 3 are executed substantially independently of each other.
  • inlet valves 4 and exhaust valves 5 are provided which are mechanically actuated by means of rotatably mounted about bearing axes 6 rocker arm 7.
  • the bearing shafts 6 and the rocker arms 7 are each parts of connecting mechanisms, the inlet and outlet valves 4 and 5 with a in the embodiment according to Fig. 1 not shown in detail Camshaft of the internal combustion engine 1 connect.
  • each connecting mechanism also includes a respective valve bridge 8 and an adjusting screw 9, which are arranged between the inlet or outlet valve 4 and 5 and the associated rocker arm 7.
  • the main oil circuit comprises oil supply channels 10, which extend, inter alia, also within the bearing axles 6, the rocker arms 7 and the adjusting screws 9.
  • the internal combustion engine 1 is equipped with an EVB type engine brake device 11.
  • This includes in addition to Fig. 1 throttle elements not shown in detail in the exhaust ducts and also not shown in detail central control / regulating unit for the oil pressure in the additional oil circuit 3, per cylinder, a hydraulic additional valve control unit 12, the piston-cylinder unit in the valve bridge 8 of the respective exhaust valve. 5 is installed.
  • the additional valve control units 12 are each connected to the additional oil circuit 3, by means of which oil pressure they can be switched on and off.
  • Oil supply channels 13 ensure the supply of the auxiliary hydraulic valve control units 12 with the oil of the additional oil circuit 3.
  • a check valve 14 is arranged in each case, which in an adjusting screw 15 of a stop 16 (see Fig. 2 and 3 ), to which the valve bridge 8 of the respective exhaust valve 5 abuts, is integrated. By means of the stop 16, a temporary hydraulic connection between the additional oil circuit 3 and the additional valve control unit 12 is produced.
  • An oil pressure or an oil pressure level of the additional oil circuit 3 can be changed by means of an oil pressure variation means 17, which is inserted into an oil feed line 18 of the additional oil circuit 3.
  • the oil pressure varying means 17 may be, for example, a pressure reducing valve or an oil pump.
  • This task is in turn through the in Fig. 1 not perceived with illustrated central control unit of the engine brake device 11.
  • the hydraulic valve auxiliary units 12 are switched on or off, or controlled or regulated in their hereinafter explained in more detail effect on the displacement position of the respective exhaust valve 5.
  • the braking force of the engine brake device 11 can be adjusted very fine.
  • the rocker arm 7 acts on the adjustable 8 and countered by the nut 19 adjusting screw 9 with a ball joint articulated at its free end Stützkalotte 20 on the valve bridge 8 a.
  • the valve bridge 8 is used in the in Fig. 2 and 3 11 except for controlling the exhaust valve 5 required for the operation of the engine brake device 11 also for controlling a further exhaust valve 21 disposed in the same cylinder of the internal combustion engine 1 as the exhaust valve 5.
  • the exhaust valves 5 and 21 are provided with a shaft 22 and 23, respectively mounted axially movable in the cylinder head 24 and acted upon by a closing spring 25 and 26 with a certain biasing force in the closing direction.
  • the closing force of the closing spring 25 is designated F Fed .
  • the exhaust valve 5 associated with the engine brake device 11 includes, as already stated above, the hydraulic additional valve control unit 12, the control piston 27 is guided axially movably in a provided in the valve bridge 8 cylinder bore 28.
  • the control piston 27 is supported at the upper end of the shaft 22 of the exhaust valve 5.
  • the additional valve control unit 12 also includes an adjusting spring 29, which is arranged on a side facing away from the shaft 22 side of the control piston 27 in a control pressure chamber 30 and the control piston 27 presses against the shaft 22.
  • the spring force of the adjusting spring 29 serves to track the control piston 27th
  • the control pressure chamber 30 is provided with an oil passage 31, by means of which oil of the additional oil circuit 3 enter the control pressure chamber 30 and can escape from the control pressure chamber 30 again.
  • the oil passage 31 extends from the control pressure chamber 30 to a region of a surface of the valve bridge 8, which bears against the stop 16 during a partial cycle duration. This operating situation with valve abutment abutting stop 16 is in FIG Fig. 2 and 3 shown.
  • the adjusting screw 15 of the stopper 16 is provided with an oil supply passage 32 which is connected to the oil supply passage 13 of the auxiliary oil circuit 3.
  • the check valve 14 is disposed within this oil supply passage 32. It includes a ball and a ball seat, as well as a Kugelhubanschlag.
  • the oil supply passage 32 opens into an outlet opening 33 which is arranged concentrically with the oil passage 31 at abutting the valve bridge 8 stop 16.
  • oil of the additional oil circuit 3 can pass via the oil supply channel 13, the oil supply channel 32, the oil channel 31 into the control pressure chamber 30 of the auxiliary hydraulic valve control unit 12.
  • the mode of operation of the engine brake device 11 will be described in more detail below.
  • the Throttle element placed in throttle position in the exhaust passage, whereby accumulates exhaust gas in the exhaust passage between the exhaust valve opening of one or more cylinders and the throttle element.
  • a pneumatic force F pn results, which counteracts the closing force F Fed of the closing spring 25 and under certain circumstances causes the mentioned intermediate opening of the outlet valve 5.
  • This pneumatic force F pn is supported by a hydraulic force F Hyd , which adjusts itself with the oil of the additional oil circuit 3 due to the admission of the control pressure chamber 30. If the sum of the pneumatic force F pn and the hydraulic force F Hyd is greater than the closing force F Fed of the closing spring 25, the intermediate opening of the outlet valve 5 takes place.
  • the strength of the hydraulic force F Hyd can thus be used to regulate this process.
  • the exhaust valve 5 opens more or less or - at very low oil pressure in the additional oil circuit 3 - not at all.
  • the control piston 27 follows the opening movement of the exhaust valve 5 due to the spring force of the adjusting spring 29 and the oil pressure force, thereby increasing the volume of the control pressure chamber 30 at the same time. It flows oil from the additional oil circuit 3 in the control pressure chamber 30 after. Since the oil can not flow from the control pressure chamber 30 back into the oil supply passage 13 of the additional oil circuit 3 due to the check valve 14, the control piston 27th against the closing force F Fed of the closing spring 25 in position and thus also the mechanically coupled to the control piston 27 outlet valve 5 held in the intermediate open position.
  • the control piston 27 is thus hydraulically blocked in the valve bridge 8, when the exhaust valve 5 after the first cycle or at the beginning of the second cycle at the latest intermediate opening in the course of the second and third clock tends to close again.
  • the pneumatic force F pn alone is not sufficient to effect an intermediate opening of the outlet valve 5 against a correspondingly high closing force F Fed . Due to the set low oil pressure in the additional oil circuit 3, the hydraulic auxiliary valve control unit 12 is thus switched off or deactivated during normal-fire engine operation.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
EP09007579A 2008-07-11 2009-06-09 Dispositif de frein moteur et procédé de freinage moteur doté d'une unité de commande supplémentaire à soupape Active EP2143895B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102008032774A DE102008032774A1 (de) 2008-07-11 2008-07-11 Motorbremseinrichtung und Verfahren zur Motorbremsung mit einer Ventil-Zusatzsteuereinheit

Publications (2)

Publication Number Publication Date
EP2143895A1 true EP2143895A1 (fr) 2010-01-13
EP2143895B1 EP2143895B1 (fr) 2011-12-21

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ID=41138706

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EP09007579A Active EP2143895B1 (fr) 2008-07-11 2009-06-09 Dispositif de frein moteur et procédé de freinage moteur doté d'une unité de commande supplémentaire à soupape

Country Status (3)

Country Link
EP (1) EP2143895B1 (fr)
CN (1) CN101624924B (fr)
DE (1) DE102008032774A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011135162A1 (fr) * 2010-04-30 2011-11-03 Wärtsilä Finland Oy Agencement de commande pour soupape d'échange gazeux dans un moteur à piston
CN104265395A (zh) * 2013-07-26 2015-01-07 皆可博车辆控制***公司 用于多气缸内燃机的空气激活供油装置
WO2017008857A1 (fr) * 2015-07-16 2017-01-19 Eaton Srl Agencement pour un ensemble dispositif de commande de soupapes

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012012875A1 (de) 2012-06-28 2014-01-02 Man Truck & Bus Ag Verfahren und Vorrichtung zum Steuern zumindest einer Bremsklappe
CN109882296A (zh) * 2015-05-12 2019-06-14 上海尤顺汽车部件有限公司 一种用于车辆缓速的发动机制动方法
CN110173314B (zh) * 2019-05-15 2023-07-18 浙江大学 一种可实现压缩释放式发动机制动的气门桥及其排气制动方法
US10876438B1 (en) 2019-08-29 2020-12-29 Zhejiang Liming Intelligent Manufacturing Co., Ltd. Braking device for electric engine

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0193142A1 (fr) * 1985-02-27 1986-09-03 Klöckner-Humboldt-Deutz Aktiengesellschaft Dispositif de frein moteur pour moteur à combustion interne
EP0407842A1 (fr) * 1989-07-12 1991-01-16 MAN Nutzfahrzeuge Aktiengesellschaft Frein moteur pour moteur à compression d'air
EP0736672A2 (fr) 1995-04-04 1996-10-09 Steyr Nutzfahrzeuge Ag Procédé de freinage moteur pour moteur à combustion interne à quatre temps
US6418720B1 (en) * 2001-08-31 2002-07-16 Caterpillar Inc. Method and a device for engine braking a four stroke internal combustion engine
WO2002095203A1 (fr) * 2001-05-22 2002-11-28 Diesel Engine Retarders, Inc. Procede et systeme de freinage moteur dans un moteur a combustion interne
WO2004059131A2 (fr) * 2002-12-23 2004-07-15 Jacobs Vehicle Systems, Inc. Procedes et appareils de freinage moteur
EP1526257A2 (fr) 2003-10-24 2005-04-27 MAN Nutzfahrzeuge Aktiengesellschaft Dispositif de frein moteur pour un moteur à combustion interne à 4 temps
WO2007078309A2 (fr) * 2005-12-28 2007-07-12 Jacobs Vehicle Systems, Inc. Procede et systeme pour frein a cycle de resistance de fuite partielle

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN100342123C (zh) * 2005-07-26 2007-10-10 马银良 排气门开启高度可变的发动机缓速器装置

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0193142A1 (fr) * 1985-02-27 1986-09-03 Klöckner-Humboldt-Deutz Aktiengesellschaft Dispositif de frein moteur pour moteur à combustion interne
EP0407842A1 (fr) * 1989-07-12 1991-01-16 MAN Nutzfahrzeuge Aktiengesellschaft Frein moteur pour moteur à compression d'air
EP0736672A2 (fr) 1995-04-04 1996-10-09 Steyr Nutzfahrzeuge Ag Procédé de freinage moteur pour moteur à combustion interne à quatre temps
EP0736672B1 (fr) 1995-04-04 1998-04-08 Steyr Nutzfahrzeuge Ag Procédé de freinage moteur pour moteur à combustion interne à quatre temps
WO2002095203A1 (fr) * 2001-05-22 2002-11-28 Diesel Engine Retarders, Inc. Procede et systeme de freinage moteur dans un moteur a combustion interne
US6418720B1 (en) * 2001-08-31 2002-07-16 Caterpillar Inc. Method and a device for engine braking a four stroke internal combustion engine
WO2004059131A2 (fr) * 2002-12-23 2004-07-15 Jacobs Vehicle Systems, Inc. Procedes et appareils de freinage moteur
EP1526257A2 (fr) 2003-10-24 2005-04-27 MAN Nutzfahrzeuge Aktiengesellschaft Dispositif de frein moteur pour un moteur à combustion interne à 4 temps
WO2007078309A2 (fr) * 2005-12-28 2007-07-12 Jacobs Vehicle Systems, Inc. Procede et systeme pour frein a cycle de resistance de fuite partielle

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011135162A1 (fr) * 2010-04-30 2011-11-03 Wärtsilä Finland Oy Agencement de commande pour soupape d'échange gazeux dans un moteur à piston
CN104265395A (zh) * 2013-07-26 2015-01-07 皆可博车辆控制***公司 用于多气缸内燃机的空气激活供油装置
WO2017008857A1 (fr) * 2015-07-16 2017-01-19 Eaton Srl Agencement pour un ensemble dispositif de commande de soupapes
US10669899B2 (en) 2015-07-16 2020-06-02 Eaton Intelligent Power Limited Arrangement for a valve train assembly

Also Published As

Publication number Publication date
EP2143895B1 (fr) 2011-12-21
CN101624924A (zh) 2010-01-13
DE102008032774A1 (de) 2010-01-14
CN101624924B (zh) 2013-10-30

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