EP2444602B1 - Motorbremsvorrichtungen und -verfahren - Google Patents

Motorbremsvorrichtungen und -verfahren Download PDF

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Publication number
EP2444602B1
EP2444602B1 EP11006451.6A EP11006451A EP2444602B1 EP 2444602 B1 EP2444602 B1 EP 2444602B1 EP 11006451 A EP11006451 A EP 11006451A EP 2444602 B1 EP2444602 B1 EP 2444602B1
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EP
European Patent Office
Prior art keywords
braking
engine
valve
piston
cam
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.)
Not-in-force
Application number
EP11006451.6A
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English (en)
French (fr)
Other versions
EP2444602A1 (de
Inventor
Zhou Dr. Yang
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.)
Shanghai Universoon Auto Parts Co Ltd
Yang Zhou
Original Assignee
Shanghai Universoon Auto Parts Co Ltd
Yang Zhou
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
Priority claimed from US12/348,320 external-priority patent/US8065987B2/en
Priority claimed from US12/348,317 external-priority patent/US7984705B2/en
Priority claimed from CN200920142242U external-priority patent/CN201372829Y/zh
Priority claimed from CN 200910056200 external-priority patent/CN101994538B/zh
Priority claimed from CN 200910056670 external-priority patent/CN101994539B/zh
Priority claimed from CN 200910194870 external-priority patent/CN102003241B/zh
Priority claimed from CN 200910194871 external-priority patent/CN102003242B/zh
Priority claimed from CN 200910194868 external-priority patent/CN102003239B/zh
Priority claimed from CN 200910194869 external-priority patent/CN102003240B/zh
Priority claimed from CN 200910194859 external-priority patent/CN102003238B/zh
Priority claimed from CN 200910194857 external-priority patent/CN102003236B/zh
Priority claimed from CN 200910194858 external-priority patent/CN102003237B/zh
Priority claimed from CN 200910195285 external-priority patent/CN102011622B/zh
Application filed by Shanghai Universoon Auto Parts Co Ltd, Yang Zhou filed Critical Shanghai Universoon Auto Parts Co Ltd
Publication of EP2444602A1 publication Critical patent/EP2444602A1/de
Publication of EP2444602B1 publication Critical patent/EP2444602B1/de
Application granted granted Critical
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F01L1/02—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
    • 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
    • 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
    • F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
    • F01L1/267—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder with means for varying the timing or the lift of the valves
    • 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
    • F01L13/065—Compression release engine retarders of the "Jacobs Manufacturing" type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
    • F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
    • F02D13/04—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation using engine as brake
    • 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
    • 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
    • F01L1/047—Camshafts
    • F01L1/053—Camshafts overhead type
    • F01L2001/0537—Double overhead camshafts [DOHC]
    • 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
    • F01L2305/00—Valve arrangements comprising rollers
    • 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
    • F01L2800/00—Methods of operation using a variable valve timing mechanism
    • 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
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/03—Auxiliary actuators
    • F01L2820/031—Electromagnets
    • 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
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/03—Auxiliary actuators
    • F01L2820/033—Hydraulic engines

Definitions

  • An additional disadvantage of the know arrangement is that it does not have an easy way or a proper lash adjusting means to set the valve lash.
  • US 2005/000499A1 (RUGGIERO BRIAN ET AL, JAN. 6, 2005 ) disclosed a rocker brake with one braking piston in the rocker arm.
  • FIG. 2 is a function chart illustrating the general relationship between the normal engine operation 20 and the added engine braking operation 10 according to one version of the present invention.
  • the small cam lobe(s) on the exhaust cam 230 are skipped, as shown in block 240, due to a gap 234 among the valve train components, to produce the main exhaust valve lift profile 220m for the normal engine valve event 20N.
  • the engine brake control means 50 controls the motion of the engine brake actuation means 100 between an inoperative position 0 and an operative position 1.
  • FIG. 5A When engine brake is needed, the engine brake control means 50 is turned on ( FIG. 5A ) and the engine oil is transmitted to the engine brake actuation means 100 through the braking fluid circuit.
  • FIG. 4B shows that the engine oil from flow passage 214 can get to the bottom of the lash adjusting screw 110 because its stem 191 is smaller than the bore 190 of the ball-locking piston 165 in which the braking piston 160 slides. Oil pressure overcomes the force of spring 198 and pushes up the rocker arm 210 for a clockwise rotation to take up the gap 234 between the cam 230 and the cam follower 235 ( FIG. 4B ).
  • the valve body 60 has the inlet port 111, the outlet port 211 and the discharge port 222.
  • a ball 67 is mounted in a bore 75b and separates the inlet port 111 and the outlet port 211.
  • a movable valve member for example, a cylindrical body 64 is disposed in a bore 75a to separate the outlet port 211 and the discharge port 222.
  • a plunger 66 is disposed between the cylindrical body 64 and the ball 67.
  • the three ports are separated or sealed from each other by O-rings 65 and 68.
  • a screen 69 can be installed before the inlet port 111 to prevent any contaminants from getting into the valve.
  • the ball-locking piston 165 is biased up by a spring 177r and a gap 185 is formed between the ball-locking piston 165 and the reset stop 182.
  • the gap 185 is so designed that the ball-locking piston 165 will not touch the reset stop 182 during the normal engine operation.
  • the engine brake reset means 150 may work without the reset spring 177r because the ball-locking piston 165 can be unseated by the reset stop 182 to reset and turn off the engine brake actuation means 100.
  • the ball-locking piston 165 When the ball-locking piston 165 is unseated, there may be oil leakage through the annular gap between the small piston or stem of the ball-locking piston 165 and the bore 450 in the valve bridge 400.
  • the engine brake reset means 150 can also be disabled by removing the reset stop 182, then the motion of the whole cam is transmitted to the exhaust valves 300 to produce an enlarged main valve lift profile and a secondary valve lift profile for the engine braking operation. Without the reset stop 182, the reset spring 177r is needed to unlock the ball-locking device and turn off the engine brake.
  • FIGS. 17A and 17B are schematic diagrams of another embodiment, which is not part of the claimed invention with the engine brake actuation means 100 integrated into the valve bridge 400.
  • the engine brake actuation means 100 is a ball-locking device similar to that shown in FIGS. 11A and 11B .
  • a plurality of balls 175 are restrained by three surfaces on three different elements of the engine brake actuation means 100.
  • the first surface is the tapered surface 192 on the braking piston 160 that is slidably disposed in a large bore 190 in the valve bridge 400.
  • the second surface is the bottom flat surface of the bore 190, and the third surface on the ball-locking piston or plunger 165 that is slidably disposed in a small bore 450 in the valve bridge.
  • the engine brake reset means 150 includes the ball-locking piston 165 and a reset stop 182 on the engine cylinder head 500.
  • Oil pressure at the second level or higher overcomes the load of the braking springs 177 and pushes the braking pistons 160 down and out of the bores 190 to the exhaust valves 300.
  • the braking pistons 160 are at the operative position now and their motion or stroke is limited by the exhaust valves 300 and equal to the gap 234 as shown in FIG. 18B .
  • the control fluid displaced the braking pistons 160 takes up the gap 234 and forms a hydraulic linkage between the valve bridge 400 and the exhaust valves 300.
  • FIG. 20D shows a different braking piston assembly that can be used for the embodiment which is not part of the claimed invention, shown in FIGS. 20A and 20B .
  • the two braking pistons 160a and 160b are biased toward each other by the braking springs 177a and 177b that are held and guided by a screw 148 and a screw nut 149.
  • the inoperative surface 145 and the operative surface 140 are cylindrical.
  • the two braking pistons 160a and 160b are separated by a clip ring 159 ( FIG. 20D ) that can be mounted in a groove (not shown) at the center of the bore 415 ( FIGS. 20A and 20B ).
  • 25A shows the retracted position of the toggle device where the two pins guided in the slot 137 that is cut through a guiding piston 162 are pushed to the left by the spring 156.
  • the guiding piston 162 slides in a horizontal bore 260 in the braking housing 210.
  • the slot 137 in the guiding piston 162 has a width that is about the same as or slightly larger than the diameter of the two pins and a length that is smaller than the diameter of the bore 190. There will be always contact (no separation) among the braking piston, the lower pin, the upper pin and the adjusting screw due to the upward force of the spring 177 that is secured to the brake housing 210 with at least one screw 179.
  • the engine braking control means When engine brake is needed, the engine braking control means is turned on and oil pressure can push both pistons 162 and 164 to the right against the preloads of the spring 156 and 177.
  • the actuation piston 164 can be moved to the right further to lock the two pins or toggles 184 and 186 in a straight position, aligned with the adjusting screw 110b and the braking piston 160, as shown in FIG. 25B .
  • the toggle device is locked to its extended position on the operative position.
  • the motion limiting means for this toggle device is unique.
  • the angle between the two pins or toggles 184 and 186 decides the height difference 130, while the angle itself is controlled by the two pistons 162 and 164.
  • the bleeding orifice 168 in the guiding piston 162 is designed to eliminate hydraulic lock.
  • FIG. 35 is a schematic diagram of another engine braking apparatus, which is not part of the claimed invention, with a wedge system at the "Off" position.
  • the only difference from FIG. 34 is that the slant surface 140 on the braking piston160 is perpendicular to the brake actuation linkage 210.

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  • 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)

Claims (14)

  1. Vorrichtung zum Umschalten eines Verbrennungsmotors von einem normalen Motorbetrieb zu einem Motorbremsbetrieb, wobei der Motor einen Auslassventiltrieb mit zwei Auslassventilen (300), einer Ventilbrücke (400), einem Kipphebel (210) und einem AuslassVentilheber (200) mit einem Auslassnocken (230) mit einem Auslassnockenbuckel (220) zum zyklischen Öffnen und Schliessen der beiden Auslassventile (300) enthält, dadurch gekennzeichnet, dass die Vorrichtung aufweist: (a) einen Aktuator (100), der ein in den Auslassventiltrieb integriertes hydraulisches System enthält, wobei das hydraulische System einen einzigen Bremskolben (160) in gleitbeweglicher Anordnung zwischen einer Ruhestellung und einer Betriebsstellung in der Ventilbrücke (400) aufweist; wobei der Bremskolben (160) in der Ruhestellung zurückgezogen und von dem normalen Motorbetrieb entkoppelt und keiner Last von einem der beiden Auslassventile (300) ausgesetzt ist und wobei der Bremskolben (160) in der Betriebsstellung ausgefahren ist und nur eines (300a) der beiden Auslassventile (300) für den Motorbremsbetrieb öffnet; und (b) eine Steuerungsvorrichtung (50) zum Bewegen des Bremskolbens (160) zwischen der Ruhestellung und der Betriebsstellung.
  2. Vorrichtung nach Anspruch 1, wobei das hydraulische System ausserdem ein Strömungsregelungsventil (51) und einen Bremsflüssigkeitskreislauf in dem Auslassventiltrieb enthält.
  3. Vorrichtung nach Anspruch 1 oder 2, wobei der Aktuator (100) ausserdem einen zugeordneten Ventilheber (200b) enthält, wobei der zugeordnete Ventilheber (200b) einen Bremsnocken (230b) enthält, der Bremsnocken (230b) einen Bremsnockenbuckel (232) hat und der Bremsnockenbuckel (232) den Bremskolben (160) betätigt, um das eine (300a) der beiden Auslassventile (300) zu öffnen, wenn der Bremskolben (160) in der Betriebsstellung ist.
  4. Vorrichtung nach Anspruch 3, wobei der Aktuator (100) ausserdem eine Feder (198b) enthält, um den zugeordneten Ventilheber (200b) von dem Bremskolben (160) weg zu beaufschlagen.
  5. Vorrichtung nach einem der Ansprüche 1 bis 4, bei welcher der Aktuator (100) ausserdem einen in den Auslassventilheber (200) integrieren Bremsventilheber aufweist, wobei der Bremsventilheber einen in den Auslassnocken (230) integrierten Bremsnockenbuckel (232) aufweist, wobei der Auslassnockenbuckel (220) des Auslassnockens (230) vergrössert ist, um die Integration des Bremsnockenbuckels (232) aufzunehmen und wobei der Bremsnockenbuckel (232) den Bremskolben (160) betätigt, um das bremsende Auslassventil (300a) zu öffnen, wenn der Bremskolben (160) in der Betriebsstellung ist.
  6. Vorrichtung nach Anspruch 5, welche ausserdem eine Motorbremsrücksetzvorrichtung (150) aufweist, um das durch den vergrösserten Auslassnockenbuckel (220) während des Motorbremsbetriebs erzeugte Ventilhubprofil zu verändern und wobei die Rücksetzvorrichtung (150) einen Rücksetzkolben (165) und mindestens einen Rücksetzströmungsdurchtritt (167) aufweist.
  7. Vorrichtung nach einem der Ansprüche 1 bis 6, welche ausserdem eine in den Aktuator (100) integrierte Ventilspieljustiervorrichtung aufweist, um ein Spiel oder einen Spalt (132) zwischen
    dem Aktuator (100) und dem einen (300a) der Auslassventile einzustellen.
  8. Vorrichtung nach einem der Ansprüche 1 bis 7, wobei die Steuerungsvorrichtung (50) ein elektro-hydro-mechanisches System aufweist, wobei das elektro-hydro-mechanische System ein Magnetventil (51) zum Bereitstellen und Unterbrechen eines Fluidstroms zu dem Bremskolben (160) aufweist und wobei der Fluidstrom die Bewegung des Bremskolbens (160) zwischen der Ruhestellung und der Betriebsstellung steuert.
  9. Vorrichtung nach einem der Ansprüche 1 bis 8, wobei die Steuerungsvorrichtung (50) ausserdem einen Strömungsablass aufweist, um den Fluidstrom von dem Bremskolben (160) abzulassen und wobei der Strömungsablass eine Entlüftungsöffnung (197) oder einen Fluidablasskanal (167) aufweist.
  10. Verfahren zum Verändern eines Motorventilhubs in einem Verbrennungsmotor zum Erzeugen eines zusätzlichen Motorventilbetriebszustands, der sich von einem normalen Motorbetrieb unterscheidet, wobei der Motor einen Motorventiltrieb mit zwei Motorventilen (300), einer Ventilbrücke (400), einem Kipphebel (210) und einem Motorventilheber (200) zum zyklischen Öffnen und Schliessen der beiden Motorventile (300) enthält, dadurch gekennzeichnet, dass Verfahren die folgenden Schritte aufweist: (a) Bereitstellen eines Aktuators (100), der ein in den Auslassventiltrieb integriertes hydraulisches System enthält, wobei das hydraulische System einen einzigen hydraulischen Kolben (160) in gleitbeweglicher Anordnung zwischen einer Ruhestellung und einer Betriebsstellung in der Ventilbrücke (400) aufweist, wobei in der Ruhestellung der hydraulische Kolben (160) zurückgezogen und von dem normalen Motorbetrieb ausgekoppelt und keiner Last von einem der beiden Motorventile (300) ausgesetzt ist und wobei der hydraulische Kolben (160) in der Betriebsstellung ausgefahren ist und nur eines (300a) der beiden Motorventile (300) für den zusätzlichen Motorventilbetriebszustand öffnet; (b) Bereitstellen einer Steuerungsvorrichtung (50) zum Bewegen des hydraulischen Kolbens (160) mit einem Fluidstrom; (c) Einschalten der Steuerungsvorrichtung (50) und Bereitstellen des Fluidstroms an dem hydraulischen Kolben (160); (d) Bewegen des hydraulischen Kolbens (160) von der Ruhestellung zu der Betriebsstellung; (e) Einwirken auf den hydraulischen Kolben (160) durch den Aktuator (100); und (f) Öffnen nur eines (300a) der beiden Motor-Ventile für den zusätzlichen Motorventilbetriebszustand.
  11. Verfahren nach Anspruch 10, bei welchem der Aktuator (100) einen zugeordneten Ventilheber (200b) enthält, wobei der zugeordnete Ventilheber (200b) einen zugeordneten Nocken (230b) enthält, und der zugeordnete Nocken (230b) einen zugeordneten Nockenbuckel (232) hat und wobei der Schritt des Einwirkens auf den hydraulischen Kolben (160) durch den Aktuator (100) ein Betätigen des hydraulischen Kolbens (160) durch den zugeordneten Nockenbuckel (223) des zugeordneten Ventilhebers (200b) enthält.
  12. Verfahren nach Anspruch 10 und 11, welches ausserdem die folgenden Schritte aufweist: (a) Bereitstellen einer Steuerungsvorrichtung (50) mit einem Strömungsablass, der eine Entlüftungsöffnung (197) oder einen Fluidablasskanal (167) hat; (b) Ausschalten der Steuerungsvorrichtung (50) und Unterbrechen des Fluidstroms zu dem hydraulischen Kolben (160); (c) Öffnen der Entlüftungsöffnung (197) oder des Fluidablasskanals (167); (d) Ablassen des Fluids von dem hydraulischen Kolben (160) durch den Fluidablass; (e) Bewegen des hydraulischen Kolbens (160) in die Ruhestellung; und f) Auskoppeln des Aktuators (100) von dem normalen Motorbetrieb und Abschalten des zusätzlichen Motorventilbetriebszustands.
  13. Verfahren nach Anspruch 10, wobei der Aktuator (100) einen in einen Nocken (230) des Motorventilhebers (200) integrieren Hilfsnockenbuckel (232) enthält, wobei ein Nockenbuckel (220) des Nockens (230) vergrössert ist, um die Integration des Hilfsnockenbuckels (232) aufzunehmen, wobei das Verfahren die folgenden Schritte aufweist: (a) Bereitstellen einer Rücksetzvorrichtung (150), um das durch den vergrösserten Nockenbuckel (220) erzeugte Ventilhubprofil zu verändern, wobei die Rücksetzvorrichtung (150) einen Rücksetzkolben (165) und einen Rücksetzströmungskanal (167) aufweist; (b) Bewegen des Rücksetzkolbens (165) und Freigeben des Rücksetzströmungskanals (167); (c) Ablassen des Fluids von dem hydraulischen Kolben (160) und Bewegen des hydraulischen Kolbens (160) von der Betriebsstellung in die Ruhestellung; (d) Entkoppeln des hydraulischen Kolbens (160) von den Motorventilen; (e) Öffnen und dann Schliessen beider Motorventile (300) mittels des vergrösserten Nockenbuckels (220) durch den Motorventilheber (200); (f) Bewegen des Rücksetzkolbens (165) und Blockieren des Rücksetzströmungskanals (167); (g) Wiederbefüllen des hydraulischen Kolbens (160) und Bewegen des hydraulischen Kolbens (160) aus der Ruhestellung zurück in die Betriebsstellung; (h) Betätigen des hydraulischen Kolbens (160) mit dem Hilfsnockenbuckel (232) durch die Ventilspieljustiervorrichtung; und (i) Öffnen eines (300a) der beiden Motorventile (300) für den zusätzlichen Motorventilbetriebszustand.
  14. Verfahren nach Anspruch 13, welches ausserdem die folgenden Schritte aufweist: (a) Bewegen des Motorventilhebers (200) mittels des vergrösserten Nockenbuckels (220) nach vorne; (b) Blockieren des Fluidstroms von der Steuerungsvorrichtung (50) zu dem hydraulischen Kolben (160); (c) Bewegen der Ventilbrücke (400) mittels des Motorventilhebers (200); (d) Öffnen des Rücksetzströmungskanals (167) und Ablassen des Fluids aus dem hydraulischen Kolben (160); (e) Bewegen des hydraulischen Kolbens (160) von der Betriebsstellung zu der Ruhestellung; (f) Entkoppeln des Aktuators (100) von den Motorventilen (300); (g) Bewegen der beiden Motorventile (300) mittels des vergrösserten Nockenbuckels (220) durch den Motorventilheber (200); (h) Zurückbewegen des MotorVentilhebers (200) und Richten des Fluidstroms von der Steuerungsvorrichtung (50) zu dem hydraulischen Kolben (160); (i) Wiederbefüllen des hydraulischen Kolbens (160) und Bewegen des hydraulischen Kolbens (160) von der Ruhestellung zurück zu der Betriebsstellung; (j) Blockieren des Rücksetzströmungskanals (167) und Betätigen des hydraulischen Kolbens (160) mittels des Nockenbuckels (232) durch die Ventielspieljustiervorrichtung und (k) Öffnen des Motor-Ventils (300a) für den zusätzlichen Motorventilbetriebszustand.
EP11006451.6A 2009-01-05 2009-12-28 Motorbremsvorrichtungen und -verfahren Not-in-force EP2444602B1 (de)

Applications Claiming Priority (14)

Application Number Priority Date Filing Date Title
US12/348,320 US8065987B2 (en) 2009-01-05 2009-01-05 Integrated engine brake with mechanical linkage
US12/348,317 US7984705B2 (en) 2009-01-05 2009-01-05 Engine braking apparatus with two-level pressure control valves
CN200920142242U CN201372829Y (zh) 2009-04-07 2009-04-07 摇臂-阀桥组合式发动机制动装置
CN 200910056200 CN101994538B (zh) 2009-08-10 2009-08-10 一种用于发动机制动的驱动机构
CN 200910056670 CN101994539B (zh) 2009-08-19 2009-08-19 一种发动机制动装置
CN 200910194859 CN102003238B (zh) 2009-08-31 2009-08-31 一种发动机制动装置
CN 200910194857 CN102003236B (zh) 2009-08-31 2009-08-31 一种制造成本低的发动机制动装置
CN 200910194871 CN102003242B (zh) 2009-08-31 2009-08-31 一种改进的发动机制动装置
CN 200910194858 CN102003237B (zh) 2009-08-31 2009-08-31 一种发动机制动的改进装置
CN 200910194868 CN102003239B (zh) 2009-08-31 2009-08-31 一种快速制动的发动机制动装置
CN 200910194870 CN102003241B (zh) 2009-08-31 2009-08-31 一种改进的用于发动机制动的驱动机构
CN 200910194869 CN102003240B (zh) 2009-08-31 2009-08-31 一种发动机制动装置的改进结构
CN 200910195285 CN102011622B (zh) 2009-09-07 2009-09-07 一种改进的发动机制动的驱动装置
EP09837091.9A EP2384396B1 (de) 2009-01-05 2009-12-28 Motorbremsvorrichtungen und -verfahren

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EP09837091.9A Division-Into EP2384396B1 (de) 2009-01-05 2009-12-28 Motorbremsvorrichtungen und -verfahren
EP09837091.9A Division EP2384396B1 (de) 2009-01-05 2009-12-28 Motorbremsvorrichtungen und -verfahren

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EP2444602A1 (de) 2012-04-25
RU2479735C1 (ru) 2013-04-20
EP2384396B1 (de) 2014-06-25
KR101290440B1 (ko) 2013-07-26
KR20110112390A (ko) 2011-10-12
EP2384396A4 (de) 2012-11-28
EP2439381A1 (de) 2012-04-11
EP2384396A2 (de) 2011-11-09
EP2439381B1 (de) 2014-09-10
BRPI0922516B1 (pt) 2020-10-06
RU2011132887A (ru) 2013-02-10

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