EP3146185B1 - Dispositif de commande de soupapes pour véhicules lourds doté d'une caractéristique de frein moteur à décompression - Google Patents

Dispositif de commande de soupapes pour véhicules lourds doté d'une caractéristique de frein moteur à décompression Download PDF

Info

Publication number
EP3146185B1
EP3146185B1 EP15723509.4A EP15723509A EP3146185B1 EP 3146185 B1 EP3146185 B1 EP 3146185B1 EP 15723509 A EP15723509 A EP 15723509A EP 3146185 B1 EP3146185 B1 EP 3146185B1
Authority
EP
European Patent Office
Prior art keywords
rocker arm
engine brake
arm assembly
exhaust valve
assembly
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.)
Active
Application number
EP15723509.4A
Other languages
German (de)
English (en)
Other versions
EP3146185A1 (fr
Inventor
Majo Cecur
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.)
Eaton Intelligent Power Ltd
Original Assignee
Eaton Intelligent Power Ltd
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 Eaton Intelligent Power Ltd filed Critical Eaton Intelligent Power Ltd
Publication of EP3146185A1 publication Critical patent/EP3146185A1/fr
Application granted granted Critical
Publication of EP3146185B1 publication Critical patent/EP3146185B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • 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
    • F01L1/12—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

Definitions

  • the present disclosure relates generally to a rocker arm assembly for use in a valve train assembly and more particularly to a rocker arm assembly that incorporates a dedicated rocker arm that acts on a single exhaust valve to perform an engine brake function.
  • CN203097985U shows an engine braking device with special cam for braking single valve.
  • WO2012078280A1 shows engine braking devices and methods.
  • WO2012162616A1 shows a primary and auxiliary rocker arm assembly for engine valve actuation.
  • Compression engine brakes can be used as auxiliary brakes, in addition to wheel brakes, on relatively large vehicles, for example trucks, powered by heavy or medium duty diesel engines.
  • a compression engine braking system is arranged, when activated, to provide an additional opening of an engine cylinder's exhaust valve when the piston in that cylinder is near a top-dead-center position of its compression stroke so that compressed air can be released through the exhaust valve. This causes the engine to function as a power consuming air compressor which slows the vehicle.
  • the exhaust valve is actuated by a rocker arm which engages the exhaust valve by means of a valve bridge.
  • the rocker arm rocks in response to a cam on a rotating cam shaft and presses down on the valve bridge which itself presses down on the exhaust valve to open it.
  • a hydraulic lash adjuster may also be provided in the valve train assembly to remove any lash or gap that develops between the components in the valve train assembly.
  • a dual exhaust rocker arm assembly constructed in accordance to one example of the present disclosure is operable in a combustion engine mode and an engine braking mode.
  • the dual exhaust valve rocker arm assembly selectively opens first and second exhaust valves and includes a rocker shaft, an exhaust valve rocker arm assembly, an engine brake rocker arm assembly and an engine brake capsule.
  • the exhaust valve rocker arm assembly has an exhaust rocker arm that receives the rocker shaft and is configured to rotate around the rocker shaft.
  • the exhaust rocker arm further defines a bore having an inner diameter.
  • the engine brake rocker arm assembly has an engine brake rocker arm.
  • the engine brake capsule is slidably received along the inner diameter of the bore of the exhaust valve rocker arm.
  • the engine brake capsule is selectively translatable upon urging by the engine brake rocker arm.
  • the engine brake capsule urges one of the first and second exhaust valves open during engine braking mode.
  • the dual exhaust valve rocker arm assembly further comprises an oil control valve that provides oil flow for actuation of the engine brake capsule from a pressurized oil supply.
  • the engine brake capsule includes an engine brake capsule piston and an engine brake capsule body.
  • a pressurized oil chamber is defined between the engine brake capsule piston and the engine brake capsule body.
  • the engine brake rocker arm is configured to act on the engine brake capsule piston which acts on the engine brake capsule body which ultimately acts on one of the engine brake exhaust valves.
  • the dual exhaust valve rocker arm assembly further comprises a valve tip positioned between one of the engine brake exhaust valves and the engine brake capsule body.
  • a lock ball assembly can include a ball lock and a ball lock spring. The ball lock spring can urge the ball lock into a groove defined on the engine brake capsule body.
  • a c-clip can be configured on the rocker arm assembly. The c-clip can limit a stroke of the engine brake capsule and provide a hard stop.
  • the dual exhaust rocker arm assembly further includes an actuator assembly configured to move the engine brake capsule between an extended and a retracted position.
  • the actuator assembly and the oil control valve are configured in the exhaust rocker arm separate from the engine brake capsule.
  • the actuator assembly includes an actuator body, an actuator check ball, an actuator needle, an actuator return spring and an actuator locking nut.
  • the actuator needle is configured to keep the actuator check ball in an open position and prevent oil pressure buildup in the engine brake capsule.
  • the actuator check ball allows one-way replenishment at every cycle into the pressurized oil chamber.
  • the oil control valve is energized open and oil pressure causes the actuator needle to move away from a corresponding seat such that the engine brake capsule is extended a predetermined length.
  • the dual exhaust rocker arm assembly includes a first adjustment screw provided on the engine brake rocker arm and a second adjustment screw provided on the exhaust rocker arm. Both of the first and second adjustment screws are adjustable to selectively provide lash settings for the dual exhaust rocker arm assembly.
  • Heavy duty (HD) diesel engines with single overhead cam (SOHC) valvetrain requires high braking power, in particular at low engine speed.
  • the present disclosure provides an added motion type De-Compression engine brake. To provide high braking power without applying high load on the rest of the valvetrain (particularly the camshaft), the present disclosure provides a dedicated rocker arm for engine brake that acts on one exhaust valve. In this regard, half of the input load is experienced compared to other configurations that have two exhaust valves opening.
  • a partial valve train assembly constructed in accordance to one example of the present disclosure is shown and generally identified at reference 10.
  • the partial valve train assembly 10 utilizes engine braking and is shown configured for use in a three-cylinder bank portion of a six-cylinder engine. It will be appreciated however that the present teachings are not so limited. In this regard, the present disclosure may be used in any valve train assembly that utilizes engine braking.
  • the partial valve train assembly 10 is supported in a valve train carrier 12 and can include three rocker arms per cylinder.
  • each cylinder includes an intake valve rocker arm assembly 20, an exhaust valve rocker arm assembly 22 and an engine brake rocker arm assembly 24.
  • the exhaust valve rocker arm assembly 22 and the engine brake rocker arm assembly 24 cooperate to control opening of the exhaust valves and are collectively referred to as a dual exhaust valve rocker arm assembly 26 ( FIG. 2 ).
  • the intake valve rocker arm assembly 20 is configured to control motion of the intake valves.
  • the exhaust valve rocker arm assembly 22 is configured to control exhaust valve motion in a drive mode.
  • the engine brake rocker arm assembly 24 is configured to act on one of the two exhaust arms in an engine brake mode as will be described herein.
  • a rocker shaft 34 is received by the valve train carrier 12 and supports rotation of the exhaust valve rocker arm assembly 22 and the engine brake rocker arm assembly 24.
  • the exhaust valve rocker arm assembly 22 can generally include an exhaust rocker arm 40, a valve bridge 42, a spigot spigot assembly 44 and an engine brake capsule 46.
  • the valve bridge 42 engages a first and second exhaust valve 50 and 52 ( FIG. 2 ) associated with a cylinder of an engine (not shown).
  • the exhaust rocker arm 40 rotates around the rocker shaft 34 based on a lift profile of a cam shaft 54.
  • the engine brake rocker arm assembly 24 can include an engine brake rocker arm 60 having an engaging portion 62.
  • the engine brake rocker arm 60 rotates around the rocker shaft 34 based on a lift provide of the cam shaft 54.
  • the configuration includes an oil control valve 70 that provides oil flow 72 for actuation from a pressurized oil supply 74.
  • Pressurized oil chamber 78 is shown inside the engine brake capsule 46.
  • the engine brake capsule 46 can include an engine brake capsule piston 80 and an engine brake capsule body 82.
  • a valve tip pin 83 is positioned between the exhaust valve 52 and the engine brake capsule body 82.
  • a c-clip 84 can provide a hard stop for the engine brake capsule body 82.
  • An engine brake rocker arm schematic 90 represents the engine brake rocker arm assembly 24 rotating as a result of cam lobe breaking 92.
  • An actuator assembly 100 includes an actuator body 102, an actuator check ball 104, an actuator needle 106, an actuator return spring 108 and an actuator locking nut 110.
  • the oil control valve 70 is closed and the engine brake capsule body 82 is completely retracted having no influence on the exhaust valves 50 and 52 motion.
  • the actuator needle 106 can keep the check ball 104 in an open position (away from corresponding seat 107) and prevent oil pressure buildup in the engine brake capsule 46.
  • the motion of the engine brake rocker arm 60 ( FIG. 2 ), or represented in FIG. 3 as the rocker arm schematic 90 will have no effect on the motion of the exhaust valve 52 when the engine is in drive mode.
  • the oil control valve 70 When the engine is in brake (no combustion) mode, the oil control valve 70 will be energized open and oil pressure will push back the actuator needle 106 and fill (extend) the engine brake capsule 46 for a predetermined length such as 4 mm. A gap between the engine brake rocker arm 60 (rocker arm schematic 90) and the exhaust valve 52 will be compensated so that motion of the engine brake rocker arm 60 controlled by the cam lobe 92 will create additional lift on the exhaust valve 52.
  • the actuator check ball 104 will allow one-way oil replenishment at every cycle into the pressurized oil chamber 78.
  • the needle 106 When de-energizing the oil control valve 70, the needle 106 will allow oil out from the pressurized oil chamber 78 and the engine brake capsule 46 will go back into a retracted position allowing driving mode (combustion) again.
  • the engine brake rocker arm assembly 24 opens the exhaust valve 52 (positioned closer to the rocker shaft 34) providing favorable force ratio allowing higher braking power.
  • the exhaust valve 52 is opened later in a compression stroke (close to top dead center), still with acceptable load on the cam lobe.
  • FIG. 4 illustrates the engine brake capsule 46 expanded or extended.
  • the gap between the engine brake capsule body 82 and the valve tip pin 83 is eliminated.
  • FIG. 5 illustrates the engine brake at maximum lift.
  • the exhaust rocker arm 40 is on the base circle while the engine brake rocker arm 60 controls the lift of the engine brake exhaust valve 52.
  • the engine brake rocker arm 60 acts on the engine brake capsule piston 80, which acts on the engine brake capsule body 82, which acts on the valve tip pin 83, which acts on the engine brake exhaust valve 52.
  • a ball lock assembly 150 includes a ball lock 152 and a ball lock spring 154.
  • the ball lock spring 154 urges (identified by force F, FIG. 7 ) the ball lock 152 into a groove 160 defined on the outer diameter of the engine brake capsule body 82.
  • the groove 160 has a depth 170 and a radius 172 configured to assure the engine brake capsule body 82 does not shake by its inertia, but rather under the load of the engine brake rocker arm 60 in engine brake mode.
  • the ball lock assembly 150 will have no impact on the engine brake capsule piston 80 expansion or retraction time.
  • a c-clip 180 is provided to limit the stroke of the engine brake capsule body 82. In this regard, the c-clip 180 provides a hard stop important for transportation.
  • a first adjustment screw 210 is provided on the engine brake arm 60.
  • a second adjustment screw 212 is provided on the exhaust arm 40.
  • a third adjustment screw 214 is provided on the intake arm 20.
  • Each of the first, second and third adjustment screws 210, 212 and 214 all provide valve lash settings according to one example of the present disclosure.
  • the engine brake capsule 46 is pushed down (as viewed in FIG. 9 ) into the collapsed position (no oil) to zero the lash in the exhaust valve 52. From this position, the first adjustment screw 210 is re-winded for exhaust brake capsule stroke and lash on the same valve.
  • the engine brake capsule 46 is made such that the difference between a fully collapsed and fully expanded length is within a narrow tolerance 220 (such as plus or minus 0.05 mm).
  • a narrow tolerance 220 such as plus or minus 0.05 mm.
  • Each of the first, second and third adjustment screws 210, 212 and 214 can have a common thread and nut size so that a common tool can be used for adjustment.
  • actuation of engine brake function is controlled by pressurized engine oil by two oil control valves 70, one for each of the three cylinders (for the example shown in FIG. 1 ).
  • the oil control valves 70 can be configured to operate independently.
  • Valve actuation components for three cylinders are incorporated in one valvetrain carrier 12 ready to be assembled on a cylinder head.
  • the configuration provides high performance engine braking without necessarily creating high load on valvetrain components by acting solely on one exhaust valve 52.
  • a dedicated rocker arm engine brake rocker arm 60
  • engine brake rocker arm 60 for engine brake, favorable rocker and force ratio transmitting lower load on the rocker shaft 34 and camshaft 54.
  • the engine brake capsule 46 is installed in and guided by an inner diameter 190 ( FIG. 6 ) defined in the exhaust rocker arm 40.
  • the present disclosure includes an engine brake capsule 46 configured in the exhaust rocker arm 40 (instead of in the engine brake rocker arm 60).
  • the configuration provides favorable packaging advantages.
  • the engine brake capsule 46 is configured to move freely along the inner diameter 190 in the exhaust rocker arm 40 while being controlled by the engine brake rocker arm 60.
  • the configuration of the present disclosure provides actuation control from the actuator assembly 100 to move the engine brake capsule 46 between an extended and retracted position.
  • the actuator assembly 100 and the oil control valve 70 ( FIG. 3 ) are configured in the exhaust rocker arm 40 and are separate from the engine brake capsule 46.
  • the ball lock assembly 150 provides drive mode retention of the engine brake capsule body 82 in drive mode.
  • FIG. 10 shows the exhaust rocker arm 40 and the engine brake rocker arm 60 on the base circle of the cam shaft 54.
  • the engaging portion 62 of the engine brake engine brake rocker arm 60 is disengaged with the engine brake capsule piston 80.
  • the engine brake capsule 46 is collapsed.
  • the schematic of FIG. 11 corresponds to the position of the dual exhaust valve rocker arm assembly 26 in FIG. 10 .
  • the oil control valve 70 is closed draining open.
  • the check ball 104 is in an open position away from its seat 107.
  • FIG. 12 shows the exhaust rocker arm 40 on maximum lift of the cam shaft 54 and the engine brake rocker arm 60 on the base circle of the cam shaft 54.
  • the engaging portion 62 of the engine brake rocker arm 60 is disengaged with the engine brake capsule piston 80.
  • An exhaust brake rocker arm lost motion spring 232 keeps the engine brake rocker arm 60 against the camshaft 54.
  • the engine brake capsule 46 is collapsed.
  • the schematic of FIG. 13 corresponds to the position of the dual exhaust valve rocker arm assembly 26 in FIG. 12 .
  • the oil control valve 70 is closed draining open.
  • the check ball 104 is in an open position away from its seat 107.
  • FIG. 14 shows the exhaust rocker arm 40 on the base circle of the cam shaft 54 and the engine brake rocker arm 60 on the base circle of the cam shaft 54.
  • the engaging portion 62 of the engine brake rocker arm 60 is engaged with the engine brake capsule piston 80.
  • the engine brake capsule 46 is expanded such that engine brake capsule body 82 touches the valve tip 83 on the valve bridge 42.
  • the schematic of FIG. 15 corresponds to the position of the dual exhaust valve rocker arm assembly 26 in FIG. 14 .
  • the oil control valve 70 is open.
  • the needle 106 is retracted.
  • the check ball 104 opens only under oil pressure from the oil control valve 70.
  • FIG. 16 shows the exhaust rocker arm 40 on the base circle of the cam shaft 54 and the engine brake rocker arm 60 rotated a distance counterclockwise from engaging a raised portion of the cam shaft 54.
  • the engaging portion 62 of the engine brake rocker arm 60 is engaged with the engine brake capsule piston 80.
  • the engine brake capsule 46 is expanded such that engine brake capsule body 82 touches the valve tip 83 on the valve bridge 42. Rigid transitioning of the engine brake rocker arm 60 motion to the exhaust valve 52 engine brake lift (opening) is shown.
  • the schematic of FIG. 17 corresponds to the position of the dual exhaust valve rocker arm assembly 26 in FIG. 16 .
  • the oil control valve 70 is open.
  • the needle 106 is retracted.
  • the check ball 104 is closed by pressure from the engine brake capsule 46.
  • FIG. 18 shows the exhaust rocker arm 40 at maximum lift on cam shaft 54 and the engine brake rocker arm 60 on the base circle of the cam shaft 54.
  • the exhaust rocker arm assembly 22 will control opening of both valves 50, 52.
  • the engine brake rocker arm 60 will be kept in place against the cam shaft 54 by the lost motion spring 232.
  • the schematic of FIG. 19 corresponds to the position of the dual exhaust valve rocker arm assembly 26 in FIG. 18 .
  • the oil control valve 70 is open.
  • the needle 106 is retracted.
  • the check ball 104 opens only by pressure from the engine brake capsule 46.
  • the engine brake capsule 46 will expand up to its hard stop for maximum extension.
  • FIG. 20 shows the exhaust rocker arm 40 and the engine brake rocker arm 60 on the base circle of the cam shaft 54. Both exhaust valves 50, 52 will close contemporary controlled by the exhaust rocker arm assembly 22.
  • the engine brake capsule 46 will be (again) fully expanded. Oil leaked out from the engine brake capsule 46 during the lift will be replenished.
  • the schematic of FIG. 21 corresponds to the position of the dual exhaust valve rocker arm assembly 26 in FIG. 20 .
  • the oil control valve 70 is open.
  • the needle 106 is retracted.
  • the check ball 104 opens only by pressure from the engine brake capsule 46.
  • the engine brake capsule 46 will expand up to its hard stop for maximum extension.

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)

Claims (10)

  1. Ensemble culbuteur à double échappement (26) pouvant fonctionner dans un mode moteur à combustion et un mode frein moteur, l'ensemble culbuteur à double échappement (26) ouvrant de façon sélective des première et seconde soupapes d'échappement (50, 52) et comprenant :
    un axe de culbuteur (34) ;
    un ensemble culbuteur à soupape d'échappement (22) ayant un culbuteur d'échappement (40) qui reçoit l'axe de culbuteur (34) et est configuré pour tourner autour de l'axe de culbuteur (34), le culbuteur d'échappement (40) définissant en outre un alésage ayant un diamètre interne (190) ;
    un ensemble culbuteur de frein moteur (24) ayant un culbuteur de frein moteur (60) ; et
    une capsule de frein moteur (46) reçue de manière coulissante le long du diamètre interne (190) de l'alésage du culbuteur d'échappement (40), dans lequel la capsule de frein moteur (46) comprend un piston de capsule de frein moteur (80) et un corps de capsule de frein moteur (82), dans lequel une chambre d'huile sous pression (78) est définie entre le piston de capsule de frein moteur (80) et le corps de capsule de frein moteur (82), dans lequel le culbuteur de frein moteur (60) est configuré pour agir sur le piston de capsule de frein moteur (80) qui agit sur le corps de capsule de frein moteur (82) qui enfin agit sur l'une des première et seconde soupapes d'échappement (50, 52), et dans lequel la capsule de frein moteur (46) se déplace en translation de façon sélective lors de la poussée par le culbuteur de frein moteur (60), la capsule de frein moteur (46), à son tour, poussant l'ouverture de l'une des première et seconde soupapes d'échappement (50, 52) en mode frein moteur ;
    dans lequel l'ensemble culbuteur à double échappement comprend en outre :
    une soupape de commande d'huile (70) qui fournit un flux d'huile pour l'actionnement de la capsule de frein moteur (46) depuis une alimentation en huile sous pression (74),
    caractérisé en ce que :
    l'ensemble culbuteur à double échappement (26) comprend :
    un ensemble bille de verrouillage (150) comprend un verrouillage à billes (152) et un ressort de verrouillage à billes (154) ;
    dans lequel le ressort de verrouillage à billes (154) de l'ensemble bille de verrouillage (150) est configuré pour pousser le verrouillage à billes (152) dans une rainure (160) définie sur le corps de capsule de frein moteur (82) pour fournir la rétention du corps de capsule de frein moteur (82) en mode combustion ;
    dans lequel, lorsque le moteur est en mode combustion, la soupape de commande d'huile (70) est fermée et le corps de capsule de frein moteur (82) est complètement rétracté et n'a aucune influence sur le mouvement des première et seconde soupapes d'échappement (50, 52) et est retenu par l'ensemble bille de verrouillage (150).
  2. Ensemble culbuteur à double échappement selon la revendication 1, comprenant en outre une pointe de soupape (83) positionnée entre l'une des première et seconde soupapes d'échappement (52) et le corps de capsule de frein moteur (82).
  3. Ensemble culbuteur à double échappement selon la revendication 1, comprenant en outre un clip en c (84) configuré sur l'ensemble culbuteur et qui limite une course de la capsule de frein moteur (46) et fournit une butée dure.
  4. Ensemble culbuteur à double échappement selon la revendication 1, comprenant en outre :
    un ensemble actionneur configuré pour déplacer la capsule de frein moteur (46) entre une position étendue et une position rétractée.
  5. Ensemble culbuteur à double échappement selon la revendication 4, dans lequel l'ensemble actionneur (100) et la soupape de commande d'huile (70) sont configurés dans le culbuteur d'échappement (40) à distance de la capsule de frein moteur (46).
  6. Ensemble culbuteur à double échappement selon la revendication 4, dans lequel l'ensemble actionneur (100) comprend un corps d'actionneur (102), une bille de retenue d'actionneur (140), une aiguille d'actionneur (106), un ressort de rappel d'actionneur (108) et un écrou de verrouillage d'actionneur (110), dans lequel l'aiguille d'actionneur (106) est configurée pour maintenir la bille de retenue d'actionneur (140) dans une position ouverte et empêche l'accumulation de pression d'huile dans la capsule de frein moteur (46).
  7. Ensemble culbuteur à double échappement selon la revendication 6, dans lequel la bille de retenue d'actionneur (140) permet un réapprovisionnement unidirectionnel à chaque cycle dans la chambre d'huile sous pression (78).
  8. Ensemble culbuteur à double échappement selon la revendication 6, dans lequel en mode frein moteur, la soupape de commande d'huile (70) est activée en ouverture et la pression d'huile amène l'aiguille d'actionneur (106) à s'éloigner d'un siège correspondant (107) de telle sorte que la capsule de frein moteur (46) est étendue d'une longueur prédéterminée.
  9. Ensemble culbuteur à double échappement selon la revendication 8, dans lequel la désactivation de la soupape de commande d'huile (70) amène l'aiguille d'actionneur (106) à laisser l'huile sortir de la chambre d'huile sous pression (78) et la capsule de frein moteur (46) à se déplacer vers la position rétractée, permettant la combustion.
  10. Ensemble culbuteur à double échappement selon la revendication 1, comprenant en outre :
    une première vis de réglage (210) prévue sur le culbuteur de frein moteur (60) ; et
    une seconde vis de réglage (212) prévue sur le culbuteur d'échappement (40) ; dans lequel les première et seconde vis de réglage (210, 212) sont positionnées de manière réglable pour fournir de façon sélective des réglages de jeu pour l'ensemble culbuteur à double échappement.
EP15723509.4A 2014-05-21 2015-05-19 Dispositif de commande de soupapes pour véhicules lourds doté d'une caractéristique de frein moteur à décompression Active EP3146185B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201462001276P 2014-05-21 2014-05-21
PCT/EP2015/060967 WO2015177127A1 (fr) 2014-05-21 2015-05-19 Dispositif de commande de soupapes pour véhicules lourds doté d'une caractéristique de frein moteur à décompression

Publications (2)

Publication Number Publication Date
EP3146185A1 EP3146185A1 (fr) 2017-03-29
EP3146185B1 true EP3146185B1 (fr) 2020-04-01

Family

ID=53189819

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15723509.4A Active EP3146185B1 (fr) 2014-05-21 2015-05-19 Dispositif de commande de soupapes pour véhicules lourds doté d'une caractéristique de frein moteur à décompression

Country Status (4)

Country Link
EP (1) EP3146185B1 (fr)
JP (1) JP6652556B2 (fr)
CN (1) CN106536878B (fr)
WO (1) WO2015177127A1 (fr)

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108779689B (zh) 2016-03-14 2021-01-15 沃尔沃卡车集团 用于控制内燃发动机中的至少一个气门的装置
AT518933B1 (de) 2016-07-20 2018-07-15 Avl List Gmbh Brennkraftmaschine mit einer ventilbetätigungseinrichtung
US10539046B2 (en) 2016-09-27 2020-01-21 Cummins Inc. Camshaft phaser/compression brake release integration with concentric camshaft
EP3669058B1 (fr) * 2017-08-14 2024-02-28 Eaton Intelligent Power Limited Configuration intégrée de frein moteur
US11549404B2 (en) 2017-08-24 2023-01-10 Eaton Intelligent Power Limited Ball engine decompression mechanism
CN111033003B (zh) 2017-08-24 2022-04-05 伊顿智能动力有限公司 球形引擎制动机构
DE102017008963A1 (de) * 2017-09-26 2019-03-28 Daimler Ag Ventiltriebvorrichtung, insbesondere für eine Brennkraftmaschine
CN110529216B (zh) * 2019-06-27 2024-04-19 浙江黎明智造股份有限公司 一种电控式发动机制动装置
EP4090837A1 (fr) 2020-01-15 2022-11-23 Eaton Intelligent Power Limited Caractéristiques de réglage de jeu pour mécanisme crénelé
SE545489C2 (en) * 2020-12-18 2023-09-26 Gnutti Carlo Sweden Ab Rocker arm valve mechanism
CN112963220B (zh) * 2021-02-08 2022-08-02 广西玉柴机器股份有限公司 集成摇臂制动机构的制动气门和制动间隙的调整方法
WO2023151871A1 (fr) * 2022-02-10 2023-08-17 Eaton Intelligent Power Limited Culbuteur intégré pour freinage de moteur avec régleur hydraulique de jeu
WO2023222254A1 (fr) * 2022-05-16 2023-11-23 Eaton Intelligent Power Limited Capsule hydraulique pour rattrapage de jeu hydraulique
CN115949483B (zh) * 2023-03-10 2023-06-13 龙口中宇热管理系统科技有限公司 一种发动机缸内制动机构及工作方法

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3705029B2 (ja) * 1999-07-30 2005-10-12 トヨタ自動車株式会社 内燃機関のバルブタイミング制御装置
KR100732445B1 (ko) * 2005-12-08 2007-06-27 현대자동차주식회사 디젤엔진용 통합 타입 엔진브레이크
US20100037854A1 (en) * 2008-08-18 2010-02-18 Zhou Yang Apparatus and method for engine braking
CN101392667B (zh) * 2008-10-30 2013-02-27 杨柳 使用单阀和阀桥的发动机制动装置和方法
CN101769185B (zh) * 2009-01-05 2012-07-25 杨柳 带有机械链接的集成式发动机制动装置及用来改变发动机气阀运动的方法
CN102011622B (zh) * 2009-09-07 2013-05-01 上海尤顺汽车部件有限公司 一种改进的发动机制动的驱动装置
CN101994538B (zh) * 2009-08-10 2013-09-04 上海尤顺汽车部件有限公司 一种用于发动机制动的驱动机构
WO2012078280A1 (fr) * 2010-11-05 2012-06-14 Sonocine, Inc. Système d'imagerie d'élastographie
WO2012162616A1 (fr) * 2011-05-26 2012-11-29 Jacobs Vehicle Systems, Inc. Ensemble de culbuteurs principal et auxiliaire pour commande des soupapes de moteur
CN203097985U (zh) * 2013-01-09 2013-07-31 上海尤顺汽车部件有限公司 专用凸轮开单气门的发动机制动装置

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
JP6652556B2 (ja) 2020-02-26
CN106536878B (zh) 2019-05-31
JP2017519157A (ja) 2017-07-13
WO2015177127A1 (fr) 2015-11-26
CN106536878A (zh) 2017-03-22
EP3146185A1 (fr) 2017-03-29

Similar Documents

Publication Publication Date Title
EP3146185B1 (fr) Dispositif de commande de soupapes pour véhicules lourds doté d'une caractéristique de frein moteur à décompression
US10858963B2 (en) Rocker arm assembly for engine braking
US9562448B2 (en) Compression-release engine brake system for lost motion rocker arm assembly and method of operation thereof
US9885263B2 (en) Compression-release engine brake system for lost motion rocker arm assembly and method of operation thereof
EP2870330B1 (fr) Dispositif de rattrapage de jeu de soupape
US7556004B2 (en) Bactrian rocker arm and engine using same
GB2540736A (en) Valvetrain for diesel engine having de-compression engine brake
US11092042B2 (en) Rocker arm assembly with valve bridge
US10690024B2 (en) Rocker arm assembly for engine braking
WO2017177102A1 (fr) Ensemble culbuteur
CN113167137A (zh) 用于引擎制动的摇臂组件
WO2022228732A1 (fr) Ensemble culbuteur
US11401839B2 (en) Rocker based bleeder engine brake
CN112639255B (zh) 具有hla的平衡横臂放气制动
US10927724B2 (en) Rocker arm assembly
US20230235686A1 (en) Rocker arm assembly with valve bridge
CN117529600A (zh) 摇臂组件

Legal Events

Date Code Title Description
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE

PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20161208

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

DAV Request for validation of the european patent (deleted)
DAX Request for extension of the european patent (deleted)
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: EXAMINATION IS IN PROGRESS

17Q First examination report despatched

Effective date: 20180302

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: EATON INTELLIGENT POWER LIMITED

REG Reference to a national code

Ref country code: DE

Ref legal event code: R079

Ref document number: 602015049800

Country of ref document: DE

Free format text: PREVIOUS MAIN CLASS: F02D0013040000

Ipc: F01L0001260000

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

RIC1 Information provided on ipc code assigned before grant

Ipc: F01L 1/26 20060101AFI20190923BHEP

Ipc: F02D 13/04 20060101ALI20190923BHEP

Ipc: F01L 13/06 20060101ALI20190923BHEP

Ipc: F01L 1/18 20060101ALI20190923BHEP

INTG Intention to grant announced

Effective date: 20191018

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

Ref country code: AT

Ref legal event code: REF

Ref document number: 1251603

Country of ref document: AT

Kind code of ref document: T

Effective date: 20200415

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602015049800

Country of ref document: DE

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200701

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20200401

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200401

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200801

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200702

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200401

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200401

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200817

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200401

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200701

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200401

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 1251603

Country of ref document: AT

Kind code of ref document: T

Effective date: 20200401

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200401

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200401

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200401

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200401

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602015049800

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200401

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200401

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200401

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200401

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200401

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200531

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200531

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200401

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200401

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200401

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200401

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200401

26N No opposition filed

Effective date: 20210112

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20200531

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20200701

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200519

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200519

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200701

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200601

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20200531

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200401

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200401

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200401

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200401

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200401

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230521

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20230419

Year of fee payment: 9