EP0383088A1 - Frein moteur pour camions - Google Patents

Frein moteur pour camions Download PDF

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Publication number
EP0383088A1
EP0383088A1 EP90101744A EP90101744A EP0383088A1 EP 0383088 A1 EP0383088 A1 EP 0383088A1 EP 90101744 A EP90101744 A EP 90101744A EP 90101744 A EP90101744 A EP 90101744A EP 0383088 A1 EP0383088 A1 EP 0383088A1
Authority
EP
European Patent Office
Prior art keywords
line
engine
cylinder
valve
brake according
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
EP90101744A
Other languages
German (de)
English (en)
Other versions
EP0383088B1 (fr
Inventor
Károly Dipl.-Ing. Szucsányi
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
Publication of EP0383088A1 publication Critical patent/EP0383088A1/fr
Application granted granted Critical
Publication of EP0383088B1 publication Critical patent/EP0383088B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/02—Conduits between injection pumps and injectors, e.g. conduits between pump and common-rail or conduits between common-rail and injectors
    • 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
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/38—Pumps characterised by adaptations to special uses or conditions
    • 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 according to the preamble of claim 1.
  • exhaust brake is known as an engine brake system.
  • a shut-off device in the exhaust By closing a shut-off device in the exhaust, the pushing-out work of the piston is increased in that a counterpressure is built up in the exhaust pipes, against which the piston must push out.
  • Engine braking systems are also known which make the compression work of the compression stroke usable for braking by blowing off in the area of the ignition TDC (decompression braking). This is usually done by slightly opening the outlet valve (but it can also be done by an additional small valve).
  • the most common decompression brake is the Jacobs brake.
  • the pump stroke is used to open the exhaust valve slightly in the TDC.
  • the device itself thus comprises a (separate) hydraulic system with master piston, driven by the cam of the pump nozzle drive (or by the valve cams or bumpers of the external engine cylinders).
  • the engine oil is used as hydraulic fluid.
  • the opening and closing of the exhaust valve is controlled by electronics and solenoid valves.
  • This additional hydraulic system is a rather complicated device. It also requires additional design measures, due to the housing containing the control and the elements, which is placed on the cylinder head. The disadvantage of this engine brake is the complex additional component.
  • the object of the invention is therefore to propose a decompression brake of the type mentioned at the outset, which is designed to be substantially simpler and therefore cheaper, d. H. which can be done without major design changes if possible. In addition, it should be easy to combine with the usual exhaust brake.
  • the injection pump as a master cylinder, there is a very simple hydraulic device in which the number of additional control devices or actuators is small.
  • actuators for example the actuating piston, can also be made smaller because of the high pressure.
  • Figure 1 shows schematically the engine brake system (the decompression brake) of the invention.
  • the exhaust valves 14 of a direct-injection diesel engine with engine cylinder 13, engine piston 15 and piston combustion chamber 16
  • the top dead center in the area of the ignition TDC
  • the energy absorbed by the engine during the compression stroke is not during of the expansion stroke is returned to the engine.
  • the opening of the exhaust valve 14 takes place via a hydraulic device, which consists of an actuating cylinder controlling the exhaust valve 7 with actuating piston 4 (acts on the thumb of the rocker arm), a control line 3 and a master cylinder with master piston 1.
  • a hydraulic device which consists of an actuating cylinder controlling the exhaust valve 7 with actuating piston 4 (acts on the thumb of the rocker arm), a control line 3 and a master cylinder with master piston 1.
  • the hydraulic actuation of the actuating pistons 4 is caused by the injection pump elements as master pistons 1.
  • Diesel fuel is used as hydraulic fluid.
  • the use of the engine's own injection pump itself as a controlled master cylinder 1 (master cylinder) is so advantageous because the start of delivery of the same before the end of the compression stroke at 15 to 30 ° KW before TDC, where the opening of the exhaust valve 14 is desired.
  • the delivery pressure achievable by the injection pump 1 is high, it reaches up to 1000 bar, and can therefore exert a sufficient opening force on the outlet valve 14. Because of the high pressure level in the actuating cylinder, the actuating piston 4 has a small (approx. 10 mm) diameter. The delivery volume (stroke volume) per working cycle of the injection pump 1 is sufficient to give the actuating piston 4 a maximum stroke of approximately 2.5 mm.
  • a switch 6 is arranged in the one present between injection pump 1 and injection nozzle 5 Injection line 2. This allows the fuel to flow unhindered to the injector 5 in the engine mode and to the actuating cylinder 4 in the braking mode. In the latter case, the first part of the injection line 2 is converted into the control line 3, more precisely 3a. The rest of the control line 3 is formed by an additional line 3b (starting from the switch 6 and leading to the actuating cylinder 4). A check valve 7 is provided in this line 3b after the switch 6. This prevents the backflow of the fuel and thus no disturbance in the injection line 2. Thus, the outlet valve 14 remains open by the actuating piston 4 of the hydraulic system. Under certain circumstances, the injection pump's own check valve may also be sufficient.
  • a valve 10 is present in a branch line 8 to the control line 3. This is acted upon by the pressure of the motor cylinder 13 via a pressure line 9.
  • the engine cylinder pressure can be influenced by an additional exhaust brake system (exhaust flap), which improves the braking performance.
  • the valve 10 controlled by the pressure of the engine cylinder 13 causes the exhaust valve 7 to close when the pressure in the engine cylinder 13 drops below a certain level.
  • the backflow of fuel from the working cylinder 4 (via a drain line 11) is prevented by the valve 10 for as long.
  • the closing of the exhaust valve 7 is initiated when the desired minimum exhaust cylinder pressure is undershot (in the exemplary embodiment at approximately 5.7 bar).
  • the drain line 11 (leak line) of the valve 10 is connected to the leak line 5 a of the injection nozzle 5.
  • the leak lines 5a, 11 lead to a hydraulic fluid reservoir 12. From this, the injection pump 1 is also fed via a line 17.
  • FIG. 2 shows the working diagram (pV diagram) of a combined compression and extension brake cycle.
  • the cylinder pressure is plotted on the ordinate and the stroke volume on the abscissa.
  • V H means stroke volume and V K compression volume).
  • the inlet valve E s closes and the compression takes place until the outlet valve 14 opens through the actuating piston 4 of the hydraulic system, as a rule before or possibly after the TDC (the latter with a small accelerator pedal pressure, ie not full delivery of the fuel quantity) (c , A ö1 ).
  • the outlet opening pressure depends, among other things, on the compression ratio of the engine, on the start of delivery of the injection pump and on the possible boost pressure. Without considering a possible boost pressure, this pressure is set at approximately 30 bar in the exemplary embodiment when the fuel quantity is full.
  • this point is approx. 15 to 30 ° KW before TDC.
  • the pressure in the engine cylinder drops to the pressure determined by the valve 10 (e, A s1 ).
  • the opening pressure of the valve 10 is suitably chosen so that it is slightly above the pressure in the exhaust pipe.
  • the pressure here is between 3 and 4.5 bar due to the closed extension brake flap.
  • the expansion begins at point e and continues until the exhaust valve is opened again by the normal charge exchange control (f).
  • the final expansion pressure runs below atmospheric pressure.
  • the charge change f - g - h - a - b is known to be characterized by a high back pressure.
  • the high-pressure and low-pressure work surfaces formed by the changes in condition are negative, that is, they destroy work.
  • the size of the negative high pressure working loop depends on the pressure built up behind the working cylinder (actuating cylinder 4). If the pressure is less than to open the outlet valve 14 immediately after the start of delivery, that is, for opening before TDC is necessary, the outlet valve 14 is opened after TDC during expansion with a decreasing pressure in the engine cylinder. This shortens the negative high pressure loop. It even becomes zero if the funding is canceled. It follows that with "accelerate" this work surface can theoretically be controlled according to the driving or braking conditions.

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)
EP90101744A 1989-02-15 1990-01-29 Frein moteur pour camions Expired - Lifetime EP0383088B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3904497 1989-02-15
DE3904497A DE3904497C1 (fr) 1989-02-15 1989-02-15

Publications (2)

Publication Number Publication Date
EP0383088A1 true EP0383088A1 (fr) 1990-08-22
EP0383088B1 EP0383088B1 (fr) 1993-05-26

Family

ID=6374111

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90101744A Expired - Lifetime EP0383088B1 (fr) 1989-02-15 1990-01-29 Frein moteur pour camions

Country Status (6)

Country Link
US (1) US5000146A (fr)
EP (1) EP0383088B1 (fr)
JP (1) JPH02233814A (fr)
DE (2) DE3904497C1 (fr)
RU (1) RU1828499C (fr)
ZA (1) ZA899937B (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1996035861A1 (fr) * 1995-05-12 1996-11-14 Caterpillar Inc. Systeme de freinage par compression
FR2737536A1 (fr) * 1995-08-04 1997-02-07 Daimler Benz Ag Frein moteur pour un moteur a combustion interne diesel
US5713331A (en) * 1994-12-21 1998-02-03 Mannesmann Rexroth Gmbh Injection and exhaust-brake system for an internal combustion engine having several cylinders
CN105386810A (zh) * 2015-12-31 2016-03-09 潍柴动力股份有限公司 一种发动机制动系统

Families Citing this family (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3909822A1 (de) * 1989-03-25 1990-09-27 Bosch Gmbh Robert Einrichtung zur betaetigung und steuerung der ventile einer brennkraftmaschine
US5215054A (en) * 1990-10-22 1993-06-01 Jenara Enterprises Ltd. Valve control apparatus and method
DE59303199D1 (de) * 1993-01-25 1996-08-14 Steyr Nutzfahrzeuge Motorbremse bei einer 4-Takt-Brennkraftmaschine eines Nutzfahrzeuges
EP0608522B1 (fr) * 1993-01-25 1995-11-15 Steyr Nutzfahrzeuge Ag Frein moteur pour moteur 4 temps de véhicule utilitaire
DE59301259D1 (de) * 1993-01-25 1996-02-08 Steyr Nutzfahrzeuge Motorbremse bei einer 4-Takt-Brennkraftmaschine eines Nutzfahrzeuges
DE4407585C2 (de) * 1994-03-08 1996-09-19 Mtu Friedrichshafen Gmbh Variable Ventilsteuerung
DE4423657C2 (de) * 1994-07-06 1997-10-02 Daimler Benz Ag Betätigungseinrichtung für ein Motorbremsventil einer Brennkraftmaschine
US5540201A (en) 1994-07-29 1996-07-30 Caterpillar Inc. Engine compression braking apparatus and method
US5647318A (en) 1994-07-29 1997-07-15 Caterpillar Inc. Engine compression braking apparatus and method
US5526784A (en) 1994-08-04 1996-06-18 Caterpillar Inc. Simultaneous exhaust valve opening braking system
DE4433258C1 (de) * 1994-09-19 1996-03-07 Daimler Benz Ag Motorbremse für eine Dieselbrennkraftmaschine
DE19514116A1 (de) * 1995-04-14 1996-10-17 Daimler Benz Ag Vorrichtung zur Steuerung von in einem Zylinder einer Brennkraftmaschine komprimierter Luft
DE19600562C1 (de) * 1996-01-09 1997-05-22 Daimler Benz Ag Direkteinspritzende Brennkraftmaschine
US5735242A (en) * 1996-04-17 1998-04-07 Cummins Engine Company, Inc. Fuel pressure activated engine compression braking system
US6104977A (en) * 1997-06-04 2000-08-15 Detroit Diesel Corporation Method and system for engine control
US6085721A (en) * 1998-04-03 2000-07-11 Diesel Engine Retarders, Inc. Bar engine brake
DE10024268B4 (de) * 2000-05-17 2012-11-29 Robert Bosch Gmbh Vorrichtung zur Benzindirekteinspritzung in einer Kolbenbrennkraftmaschine
US20030037765A1 (en) 2001-08-24 2003-02-27 Shafer Scott F. Linear control valve for controlling a fuel injector and engine compression release brake actuator and engine using same
US6854442B2 (en) * 2002-12-02 2005-02-15 Caterpillar Inc Rotary valve for controlling a fuel injector and engine compression release brake actuator and engine using same
CN100549432C (zh) * 2006-03-27 2009-10-14 曼B与W狄赛尔公司 共轨液压系统
DE102007014250A1 (de) 2007-03-24 2008-09-25 Schaeffler Kg Brennkraftmaschine mit Motorbremse
DE102007014248A1 (de) 2007-03-24 2008-09-25 Schaeffler Kg Hubkolbenbrennkraftmaschine mit Motorbremseinrichtung
DE102007033424A1 (de) 2007-07-18 2009-01-22 Man Nutzfahrzeuge Ag Selbstreinigendes Abgasnachbehandlungssystem
DE102007051302A1 (de) 2007-10-26 2009-04-30 Schaeffler Kg Hubkolbenbrennkraftmaschine mit Motorbremse und zusätzlichem Öffnen eines Auslassventils
DE102007061005A1 (de) 2007-12-18 2009-06-25 Man Nutzfahrzeuge Ag Verfahren zur Verbesserung der Hydrolyse eines Reduktionsmittels in einem Abgasnachbehandlungssystem
DE102008039504A1 (de) 2008-08-23 2010-02-25 Schaeffler Kg Hubkolbenbrennkraftmaschine mit Motorbremseinrichtung und schaltbarem Leerhubelement

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4150640A (en) * 1977-12-20 1979-04-24 Cummins Engine Company, Inc. Fluidic exhaust valve opening system for an engine compression brake
US4741307A (en) * 1987-02-17 1988-05-03 Pacific Diesel Brave Co. Apparatus and method for compression release retarding of an engine

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3367312A (en) * 1966-01-28 1968-02-06 White Motor Corp Engine braking system
US3547087A (en) * 1968-08-09 1970-12-15 White Motor Corp Engine valve control for braking operation
US4158348A (en) * 1977-06-30 1979-06-19 Mason Lloyd R System for retarding engine speed
US4398510A (en) * 1978-11-06 1983-08-16 The Jacobs Manufacturing Company Timing mechanism for engine brake
US4384558A (en) * 1981-08-03 1983-05-24 Cummins Engine Company, Inc. Engine compression brake employing automatic lash adjustment
US4697558A (en) * 1986-02-18 1987-10-06 Meneely Vincent A Compression relief engine brake
US4711210A (en) * 1986-12-29 1987-12-08 Cummins Engine Company, Inc. Compression braking system for an internal combustion engine

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4150640A (en) * 1977-12-20 1979-04-24 Cummins Engine Company, Inc. Fluidic exhaust valve opening system for an engine compression brake
US4741307A (en) * 1987-02-17 1988-05-03 Pacific Diesel Brave Co. Apparatus and method for compression release retarding of an engine

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5713331A (en) * 1994-12-21 1998-02-03 Mannesmann Rexroth Gmbh Injection and exhaust-brake system for an internal combustion engine having several cylinders
WO1996035861A1 (fr) * 1995-05-12 1996-11-14 Caterpillar Inc. Systeme de freinage par compression
FR2737536A1 (fr) * 1995-08-04 1997-02-07 Daimler Benz Ag Frein moteur pour un moteur a combustion interne diesel
CN105386810A (zh) * 2015-12-31 2016-03-09 潍柴动力股份有限公司 一种发动机制动系统

Also Published As

Publication number Publication date
JPH02233814A (ja) 1990-09-17
DE59001521D1 (de) 1993-07-01
EP0383088B1 (fr) 1993-05-26
DE3904497C1 (fr) 1990-01-25
RU1828499C (ru) 1993-07-15
US5000146A (en) 1991-03-19
ZA899937B (en) 1990-11-28

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