EP3068982A1 - Dispositif de frein-moteur pour moteur à combustion interne - Google Patents

Dispositif de frein-moteur pour moteur à combustion interne

Info

Publication number
EP3068982A1
EP3068982A1 EP14792393.2A EP14792393A EP3068982A1 EP 3068982 A1 EP3068982 A1 EP 3068982A1 EP 14792393 A EP14792393 A EP 14792393A EP 3068982 A1 EP3068982 A1 EP 3068982A1
Authority
EP
European Patent Office
Prior art keywords
switching
cam
camshaft
firing
bearing
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
EP14792393.2A
Other languages
German (de)
English (en)
Other versions
EP3068982B1 (fr
Inventor
Matthias Lahr
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.)
Mercedes Benz Group AG
Original Assignee
Daimler 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 Daimler AG filed Critical Daimler AG
Publication of EP3068982A1 publication Critical patent/EP3068982A1/fr
Application granted granted Critical
Publication of EP3068982B1 publication Critical patent/EP3068982B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F01L1/047—Camshafts
    • 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
    • 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
    • F01L1/14—Tappets; Push rods
    • 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
    • F01L1/36—Valve-gear or valve arrangements, e.g. lift-valve gear peculiar to machines or engines of specific type other than four-stroke cycle
    • F01L1/38—Valve-gear or valve arrangements, e.g. lift-valve gear peculiar to machines or engines of specific type other than four-stroke cycle for engines with other than four-stroke cycle, e.g. with two-stroke cycle
    • 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
    • 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
    • F01L2001/0476—Camshaft bearings
    • 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
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0036—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
    • F01L2013/0052—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction with cams provided on an axially slidable sleeve

Definitions

  • the invention relates to an engine brake device for an internal combustion engine of a motor vehicle, in particular a commercial vehicle.
  • EP 2 191 106 B1 already discloses an engine brake device with a camshaft having at least one cam group with at least one firing cam and at least one brake cam, with at least one cam follower associated with the firing cam, which is provided in a firing operation for actuating at least one gas exchange valve, and a cam follower associated with the brake cam, which in a braking operation for actuating the at least one
  • Gas exchange valve is provided, and with a switching device, which is intended to switch between the firing and the braking operation, known.
  • the invention is in particular the object of a cost
  • the invention relates to an engine brake device with at least one
  • Camshaft the at least one cam group with at least one
  • Firing cam and at least one brake cam having at least one of the firing cam associated cam follower, which is provided in a firing operation for actuating at least one gas exchange valve, and a brake cam associated cam follower, which is provided in a braking operation for actuating the at least one gas exchange valve, and with a switching, which is intended to switch between the firing mode and the braking mode.
  • the switching device is provided to a
  • Aktuatorik which the force for switching, for example in the form of a
  • Hydraulic pressure provides, can be dispensed with.
  • additional actuators which in principle generate an additional drag torque, thus increasing the efficiency of an internal combustion engine with such an engine braking device. This can be reduced in particular consumption of an internal combustion engine.
  • a "cam group” is to be understood as meaning a group of cams which comprises all cams provided for a working cylinder of the internal combustion engine and which has the camshaft
  • a “braking operation” is to be understood as meaning, in particular, a triggering of the gas exchange valves for a braking operation, in which a compression work within the working cylinders is used for the braking operation
  • a switching device is to be understood as meaning, in particular, a mechanism which is provided for switching over between the firing mode and the braking mode.
  • “Provided” is to be understood in particular to be specially designed and / or equipped.
  • the switching device has at least one non-rotatably, but axially displaceable associated with the camshaft link element with at least one slide track, which is intended to a rotational movement of the
  • the motor brake device preferably comprises a relative to the gate element fixedly arranged Akuator with at least one shift pin, which is intended to intervene in the at least one slide track and implement the rotational movement of the camshaft in the linear switching movement of the link element.
  • the actuator can be formed easily and inexpensively.
  • the actuator only has to be provided to bring the shift pin into engagement with the shift gate.
  • a necessary switching force is much smaller than a supporting force, which is necessary when the actuator switches directly between the firing and braking mode, for example, by acting directly on the cam follower.
  • the actuator only needs to be energized for switching between the firing and braking operation.
  • An actuator that must be permanently active during braking operation and / or firing operation in order to operate the
  • Lighting operation or to keep the braking mode switched, can be omitted.
  • the switching device has a rocker arm bearing which has a first end position assigned to the firing mode and a second end position assigned to the braking mode. This allows the
  • Switching particularly easy to be mechanically formed By such an embodiment can be achieved that determines the end position of the rocker arm storage, whether the firing mode or the braking operation is switched, whereby only the rocker arm storage from one end position to the other for switching
  • rocker arm bearing is to be understood in particular as a bearing for rocker arms for actuating the gas exchange valves, which is intended to receive and dissipate actuation forces acting upon actuation of the gas exchange valves on the rocker arms.
  • the engine brake device comprises at least two each of the cam follower having rocker arm, the
  • Actuation of the gas exchange valve by one set by the rocker arm bearing Toggle axis are pivotable.
  • rocker arm By connecting the rocker arm to the switchable between the first end position and the second end position rocker arm bearing can be achieved that, depending on the end position of a rocker arm or the other rocker arm is in operative connection with the camshaft, which easily between the
  • the rocker arm bearing is provided to be switched by means of the torque of the camshaft between the two end positions.
  • the torque of the camshaft can be used advantageously, whereby a high efficiency can be achieved.
  • the rocker arm bearing is provided to be switched by means of the torque of the camshaft between the two end positions.
  • Tilt lever bearing derived that a torque acts, which can be used to switch from one end position to the other end position.
  • the switching device has at least one spring-loaded latch engagement element, which is provided to fix the rocker arm bearing in the two end positions or end positions.
  • the switching device has at least one movably mounted locking contour element, against which the at least one
  • the latch contour element has at least two latching positions and the link element is provided to at least one
  • Retractable contour element of the latched positions to pivot at least in an intermediate position between the locking positions.
  • Rotary movement of the camshaft is effected and the Akuator the engine brake device is only intended to trigger the switching.
  • the link element has two switching positions and an actuating pin which is provided to switch the at least one locking contour element from the first engagement position to the intermediate position in the first switching position and from the second engagement position to the intermediate position in the second switching position.
  • the link element can be mechanically coupled to the catch contour element in a particularly simple manner, which makes it possible, in particular, for the switchover of the catch contour element to occur at a defined camshaft position, whereby the entire switchover can be adapted to a cam curve of the brake cam and / or the firing cam.
  • the switching device can also be used in conjunction with others
  • Valve drives are used.
  • the switching device can also be provided for switching between a part-load operation and a full-load operation. It is also conceivable to provide the switching device for switching between a firing operation and a decompression operation,
  • a valve drive device with at least one camshaft, which has at least one cam group with at least one first cam and at least one second cam, with at least one cam follower associated with the first cam, which is provided in a first operation for actuating at least one gas exchange valve , and a second cam associated cam follower, which is provided in a second operation for actuating the at least one gas exchange valve, and with a switching device, which is intended to switch between the first operation and the second operation, the switching device provided for this purpose is to convert a torque of the camshaft into a force for switching between the first operation and the second operation.
  • Fig. 1 is a perspective view of a valve train with an integrated
  • FIG. 6 shows a cross section through the valve drive along a sectional plane C-C from FIG. 4 in a switching position for the firing operation
  • FIG. 7 shows a cross section through the valve drive along the sectional plane B-B
  • Fig. 4 in a switching position for the braking operation.
  • Figures 1 to 8 show a valve train with an integrated engine brake device for an internal combustion engine of a commercial vehicle.
  • the valve train includes a
  • Camshaft 10 which is intended for a firing operation and an engine braking operation.
  • the camshaft 10 is formed as an exhaust camshaft.
  • Camshaft 10 is provided to actuate gas exchange valves 15, 16 for non-illustrated working cylinder of the internal combustion engine.
  • the internal combustion engine comprises each
  • the camshaft 10 comprises per cylinder a cam group for actuating the two gas exchange valves 15, 16. In the embodiment, only one of
  • Cam groups shown Further cam groups, not shown in greater detail, which are provided for actuating the gas exchange valves of the further working cylinders are designed analogously.
  • the cam group comprises a firing cam 11, which is intended to open the gas exchange valves 15, 16 in a firing operation, and a
  • Brake cam 12 which provided, in a braking operation of the
  • the firing cam 1 1 and the brake cam 12 have different cam curves.
  • Lighting cam 11 has an elevation 11 ', which is particularly intended to open the gas exchange valves 15, 16, while a piston is moved in the corresponding working cylinder from a bottom dead center to a top dead center to eject exhaust gas from the working cylinder.
  • the cam curve of the brake cam 12 is in principle provided to open the gas exchange valve 16 after the piston has been moved in the corresponding working cylinder from the bottom dead center to the top dead center to leave the compressed air or combustion air unused.
  • Motor brakes device has three elevations 12 ', 12', 12 "'in Figures 5 to 8.
  • the three elevations 12', 12", 12 "'of the brake cam 12 can be clearly seen .
  • the elevation 12' forms a first decompression - respectively.
  • the motor brake device shown in Figures 1 to 8 is thus designed as a 2-stroke engine brake with recharge.Of course, the engine brake device as a 4-stroke engine brake with only a brake elevation 12 'and an optional
  • valve drive device with the integrated engine braking device comprises a cam follower 13, which for the
  • Firing operation is provided, and a cam follower 14 which is provided for the braking operation.
  • the cam follower 13, which is provided for the firing operation, is provided only for an operative connection with the firing cam 11.
  • the cam follower 14, which is provided for the braking operation, is only for
  • the engine braking device For switching between the firing operation and the braking operation, the engine braking device comprises a switching device 17 which is provided between an actuation of both gas exchange valves 15, 16 by the firing cam 11 and an actuation of the individual gas exchange valve 16 by the brake cam 12 switch over (see Figure 1).
  • the switching device 17 is provided to switch between a tap of the cam curve of the firing cam 1 1 by the associated cam follower 13 and a tap of the cam curve of the brake cam 12 by the associated cam follower 14 back and forth.
  • Switching device 17 is only for switching the operation of
  • Gas exchange valves 15, 16 of a working cylinder provided.
  • the engine brake device can basically further, analog
  • the valve train comprises two rocker arms 24, 25 associated with the cam group.
  • the one rocker arm 24 is provided for the firing operation and has the cam follower 13 provided for engagement with the firing cam 11.
  • the other rocker arm 25 is provided for the braking operation and has the cam follower 14 which is provided for operative connection with the brake cam 12.
  • rocker arm 24 acts on both gas exchange valves 15, 16.
  • the rocker arm 25 provided for the braking operation acts in the illustrated
  • Embodiment according to Figures 1 to 8 of the rocker arm 25 acts in braking mode via a
  • the two rocker arms 24, 25 are separated from each other in terms of motion. Depending on whether the firing mode or the braking mode is engaged, the camshaft 10 actuates the corresponding rocker arm 24, 25, while the other rocker arm 24, 25 is decoupled from the camshaft 10.
  • the switching device 17 is provided to convert a torque of the camshaft 10 into a force for switching between the firing operation and the braking operation. For driving by means of a control and not shown
  • the switching device 17 comprises an electromagnetic actuator 21, not shown, by means of which the switching can be triggered. Except for the actuator 21, which is provided only for triggering the switching, the switching device 17 is completely mechanically formed.
  • the switching device 17 comprises a rotationally fixed, but axially displaceable with the
  • the link element 18 has a first slide track 19, which is used for switching from the firing in the Braking operation is provided, and a second slide track 20, which is provided for switching from the braking operation in the firing mode.
  • the slide tracks 19, 20 are offset on the link element 18 by a corresponding angle to each other.
  • Each of the slide tracks 19, 20 has an angular extent corresponding to its function.
  • the slide tracks 19, 20 have, not designated in the figures, each a single track segment, a switching segment and a Ausspursegment on.
  • the circumferentially directed single track segments each have an increasing link track depth.
  • the switching segments which have a substantially constant link path depth, have an axial component.
  • the Ausspursegmente each have a decreasing link path depth.
  • the switching segments of the cam tracks 19, 20 are provided to implement a rotational movement of the camshaft 10 in a, relative to a rotational axis 29 of the camshaft 10, axial switching movement of the link element 18.
  • the releasable by means of the slide tracks 19, 20 switching movements are oriented in opposite directions, i. the one slide track 19 is to
  • the link element 18 has two discrete switching positions, between which it can be switched by means of the slide tracks 19, 20. In the embodiment shown, triggered by the slide track 19 switching movement leads to a switch from
  • Belessnessungs peaceful in the braking mode and according to a switching movement of the slide track 20 to a switch from braking operation in the firing mode.
  • the actuator 21, which is provided for triggering the switching, is arranged stationary relative to the link element 18 which is rotatably arranged by the camshaft 10.
  • the valve train has a housing 44, shown in FIG. 2, with which the actuator 21 is fixedly connected.
  • the actuator 21 includes a switching pin 22, which in an extended state in the respective slide track 19, 20 of the
  • Gate element 18 engages. To trigger the switching of the switching pin 22 is extended. Subsequently, the switching pin 22 via the corresponding
  • Cam followers 13, 14, the switching device 17 a Kipphebellagerung 23, which has a firing operation associated with the first end position and a braking operation associated with the second end position.
  • the rocker arm bearing 23 is used in particular for supporting the rocker arms 24, 25 and defines a respective one for the rocker arm 24
  • the rocker arm bearing 23 comprises a bearing element 32 on which the rocker arms 24, 25 are mounted (compare FIGS. 1 and 4).
  • the bearing element 32 itself is pivotally mounted.
  • a bearing axis 33 about which the bearing element 32 is pivotable, is arranged parallel to the Kipphebelachsen 30, 31.
  • the bearing element 32 is mounted relative to the housing 44 of the valve drive.
  • the bearing element 32 is designed in the form of a U-shaped bracket, wherein ends 45, 45 'of the bearing element 32, which parallel to the axis of rotation 29 of the
  • Camshaft 10 are used to support about the bearing axis 33, and wherein the rocker arms 24, 25 to a substantially parallel to the camshaft 10th
  • the bearing axis 33 of the bearing element 32 is offset parallel to the axis of rotation 29 of the camshaft 10 oriented (see Figure 2). In the first end position provided for the firing operation cam follower 13 in constant contact with the
  • Firing cam 1 1 The intended for braking operation cam follower 14, however, is lifted from the brake cam 12, whereby the brake cam 12 passes without effect under the cam follower 14 ( Figures 1 to 6). Conversely, in the second end position, the cam follower 14 provided for the braking operation is in constant contact with the brake cam 12, while the cam follower 13 provided for the firing operation is lifted from the firing cam 11, whereby the Firing cam 1 1 ineffective under the cam follower 13 passes ( Figures 7 and 8).
  • the rocker arm bearing 23 is provided by means of the rotational movement of the
  • Camshaft 10 to be switched. If the bearing element 32 is switched to the first end position, acts upon actuation of the gas exchange valves 15, 16 through the
  • Firing cam 11 on the support member 32 is basically a force which is directed in the direction of the second end position ( Figures 1 to 6). If the bearing element 32 is connected in the second end position, upon actuation of the gas exchange valve 16 by the brake cam 12 acts on the bearing element 32 is basically a force which is directed in the direction of the first end position ( Figures 7 and 8).
  • Gas exchange valves 15, 16 are actuated, a different force on the
  • the bearing axis 33 of the bearing element 32 is operatively disposed between the two rocker shafts axes 30, 31. If the one rocker arm 24 is actuated, resulting from the actuation force of this rocker arm 24 acting on the bearing member 32 torque, which is directed with respect to the bearing axis 33 of the bearing member 32 in the opposite direction as the resulting from the operating force of the other rocker arm 25 torque which acts on the bearing member 32 when the other rocker arm 25 is operated. Since the actuation force results in each case from the torque of the camshaft 10 and the torque on the bearing element 32 again from the actuation force, the rocker arm bearing 23 is switched by means of the rotational movement of the camshaft 10.
  • the switching device 17 a For fixing the rocker arm bearing 23, the switching device 17 a
  • the latching engagement element 26 is mounted axially movable relative to the bearing element 32.
  • the switching device 17 has a spring element 39, which is arranged between the bearing element 32 and the latch engagement element 26.
  • the switching device 17 For operative connection with the latching engagement element 26, the switching device 17 comprises a latching contour element 27, against which the latching engagement element 26 is supported.
  • the latching engagement element 26 For positive connection with the latching engagement element 26 has the
  • Rastkonturelement 27 a latching contour with two, lying between two stops 34, 35 recesses 36, 37. Between the two recesses 36, 37 is a survey 38.
  • the first recess 36 which is assigned to the first end position in the firing mode, between the first stop 34 and the survey 38.
  • the second recess 37 which is associated with the second end position in braking mode , lies between the second stop 35 and the elevation 38.
  • the recesses 36, 37 define two latching positions in which the latch engagement element 26 and the
  • Lock contour element 27 are positively connected with each other.
  • a pivoting movement of the bearing element 32 is limited by the two mechanical stops 34, 35, which define the two end positions of the rocker arm bearing 23.
  • the stops 34, 35 limit the pivotal movement of the bearing element 32, by the
  • Stop 35 abuts the bearing element 32 and the stop 34 on
  • Rasteingriffselement 26 is present. Accordingly limit the stops 34, 35, the pivotal movement of the bearing element 32 from the first end position in
  • the latching engagement element 26 is movably connected to the bearing element 32. During a movement of the bearing element 32 from one end position to the other end position, the latching engagement element 26 is moved by the one recess 36, 37 over the elevation 38 into the other recess 36, 37. In the end positions, the latching engagement element 26 and the locking contour element 27 fix the
  • a spring force which provides the spring element 39 supported between the latching engagement element 26 and the bearing element 32 is sufficiently large to support the torque resulting from the actuating force of the gas exchange valves 15, 16 against the elevation 38, so that the
  • Rasteingriffselement 26 does not change from one recess 36, 37 in the other recess 36, 37.
  • the latching contour element 27 is movably mounted.
  • the locking contour element 27 has a
  • Bearing axis 40 which lies in the region of the survey 38 of the locking contour.
  • the bearing axis 40 for the locking contour element 27 forms the elevation 38 between the two recesses 36, 37, i. the catch contour is partially formed by the bearing axis 40. If the bearing element 32 moves from one end position to the other end position, a virtual center line of the
  • Rasteingriffselements 26 over the bearing axis 40 of the locking contour element 27 away.
  • the bearing shaft 40 is thus between the two recesses 37, 37, which the
  • the movably mounted locking contour element 27 is between the first engagement position which is assigned to the firing mode (FIGS. 1 to 6) and the second one
  • the bearing element 32 In the first engagement position of the locking contour element 27, the bearing element 32 is in its first end position in the firing mode, wherein the latching engagement element 26 engages in the first recess 36 of the latching contour. In the second engagement position of the locking contour element 27, the bearing element 32 is in its second end position in braking operation, wherein the latching engagement element 26 engages in the second recess 37 of the latching contour. In the latching positions, one of the recesses 36, 37 of the latching contour element 27 for the latching engagement element 26 forms a global minimum into which the latching engagement element 26 is guided when the actuating force for the gas exchange valves 15, 16 is supported against the camshaft 10 via the bearing element 32 ,
  • the bearing element 32 is switched for the rocker arms 24, 25 at the next actuation of the gas exchange valves 15, 16 in the latching position corresponding end position.
  • the switching between the lighting operation and the braking operation is carried out so by the locking contour element 27 from one engagement position and in the other
  • the link element 18 is provided to the latch contour element 27 of the
  • the link element 18 and the locking contour element 27 are mechanically coupled together.
  • the protruding from the camshaft 10 link element 18 is received with an axially displaceable in the camshaft 10 shift rod 48th connected.
  • the link element 18 and the shift rod 48 are together upon engagement of the switch pin 22 in one of the slide tracks 19, 20 along the
  • Camshaft 10 protrudes.
  • the actuating pin 28 is thus also displaced along the axis of rotation 29 with the axial displacement of the shift rod 48 in its longitudinal slot 49.
  • the actuating pin 28 is provided to transmit the torque applied to the camshaft 10 to the locking contour element 27 and to pivot the locking contour element 27 by means of the torque.
  • the connecting member 48 connected to the shift rod 48 has a suitable locking device 50 with the
  • Camshaft 10 so that a corresponding position of the shift rod 48 can be held in the camshaft 10 for the braking operation or firing operation.
  • the locking contour element 27 is arranged spatially between the latching engagement element 26 and the camshaft 10. It has a the latching engagement element 26 facing side, which forms the latching contour. In addition, it has a camshaft 0 side facing, which forms an actuating contour for pivoting by means of the torque of the camshaft 10.
  • the actuating contour has two tracks 41, 42 which are offset from one another along the axis of rotation 29 of the camshaft 10. Depending on the switching position in which the link element 18 is connected, the actuating pin 28 engages the one path 41 of the actuating contour or on the other track 42 of the actuating contour. A way by which the link element 18 is axially displaceable corresponds to a distance of the tracks 41, 42, the
  • the tracks 41, 42 are formed as inclined tracks.
  • Actuation contour of the locking contour element 27 is intended to be on the
  • Actuator pin 28 acting torque of the camshaft 10 in a on the
  • the actuating pin 28 in operative connection with the actuating contour of the locking contour element 27 is provided to switch the locking contour element 27 from the first engagement position of the firing operation into the intermediate position in the first switching position of the link element 18.
  • the switching pin 22 engages in the slide track 19 and the actuating pin 28 is moved from the track 41 to the web 42.
  • the locking contour element 27 switches from the second engagement position of the braking operation in the intermediate position.
  • the switching pin 22 engages in the slide track 20 and the actuating pin 28 is moved from the web 42 to the web 41.
  • the actuating pin 28 is therefore only provided in each case, the locking contour element 27 in the
  • the intermediate position is formed in the illustrated embodiment as a middle position between the two latching positions. If the latching contour element 27 is pivoted into the middle position, the latching engagement element 26 moves in the latching contour. The latching engagement element 26 moves within the locking contour of the corresponding recess 36, 37 on the survey 38. Since at the same time
  • Lock contour element 27 is pivoted, the intermediate position forms an unstable position. From the intermediate position, the latching engagement element 26 is then guided into the other engagement position when the actuation force on the gas exchange valves 15, 16, which results from the rotation and the torque of the camshaft 10, at the next actuation of the gas exchange valves 15, 16 via the support member 32nd is supported against the camshaft 10.
  • the switching between the firing mode and the braking operation thus takes place in two steps.
  • the torque and the rotational movement of the camshaft 10 via the link element 18, the latch contour element 27 and the latch engagement element 26 are transmitted to the bearing element 32 and cause the latch engagement element 26 of the corresponding latching position in the first step.
  • the switching device 17 comprises a second latch engagement element 26 'and a second latch contour element 27', which are also connected by means of the link element 18.
  • the link element 18 has for this purpose a second actuating pin 28 'and spring elements 39 ", which is provided for an operative connection with the second latch contour element 27' .
  • the two latch contour elements 27, 27 ' act in parallel.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

L'invention concerne un dispositif de frein-moteur pourvu d'au moins un arbre à cames (10), lequel comprend au moins un groupe de cames doté d'au moins une came de chauffe (11) et d'au moins une came de frein (12). Le dispositif est également pourvu d'au moins un suiveur de came (13) associé à la came de chauffe (11) et prévu, en mode chauffe, pour actionner au moins une soupape d'échange des gaz (15, 16), et d'un suiveur de came (14) associé à la came de frein (12)) et prévu, en mode freinage, pour actionner la ou les soupapes d'échange des gaz (15, 16), et d'un dispositif de basculement (17), lequel est prévu pour mettre en œuvre le basculement entre le mode chauffe et le mode freinage, le dispositif de basculement (17) étant prévu pour convertir un couple de l'arbre à cames (10) en une force permettant le basculement entre le mode chauffe et le mode freinage.
EP14792393.2A 2013-11-13 2014-10-25 Dispositif de frein-moteur pour moteur à combustion interne Active EP3068982B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201310019000 DE102013019000A1 (de) 2013-11-13 2013-11-13 Motorbremsvorrichtung für eine Brennkraftmaschine
PCT/EP2014/002884 WO2015070949A1 (fr) 2013-11-13 2014-10-25 Dispositif de frein-moteur pour moteur à combustion interne

Publications (2)

Publication Number Publication Date
EP3068982A1 true EP3068982A1 (fr) 2016-09-21
EP3068982B1 EP3068982B1 (fr) 2017-05-03

Family

ID=51844666

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Application Number Title Priority Date Filing Date
EP14792393.2A Active EP3068982B1 (fr) 2013-11-13 2014-10-25 Dispositif de frein-moteur pour moteur à combustion interne

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US (1) US9874123B2 (fr)
EP (1) EP3068982B1 (fr)
JP (1) JP6225258B2 (fr)
CN (1) CN105723055B (fr)
DE (1) DE102013019000A1 (fr)
WO (1) WO2015070949A1 (fr)

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CN106133286B (zh) * 2014-02-14 2018-07-06 伊顿(意大利)有限公司 用于发动机制动的摇臂组件
DE102014008378A1 (de) 2014-06-05 2015-12-17 Daimler Ag Motorbremsvorrichtung für eine Brennkraftmaschine
DE102015009877A1 (de) 2015-07-29 2017-02-02 Daimler Ag Ventiltriebvorrichtung, Brennkraftmaschine mit einer Ventiltriebvorrichtung und Verfahren zum Betrieb einer Ventiltriebvorrichtung
SE539832C2 (en) * 2016-04-28 2017-12-12 Scania Cv Ab A valve drive for an internal combustion engine with variable control of valves
DE102016009343A1 (de) 2016-08-02 2017-02-09 Daimler Ag Verfahren zum Starten einer Verbrennungskraftmaschine eines Kraftfahrzeugs, insbesondere eines Kraftwagens
DE102017009541A1 (de) 2017-10-13 2019-04-18 Daimler Ag Ventiltrieb für eine Brennkraftmaschine eines Kraftfahrzeugs
DE102017009535A1 (de) 2017-10-13 2019-04-18 Daimler Ag Ventiltrieb für eine Brennkraftmaschine eines Kraftfahrzeugs
DE102017011855A1 (de) 2017-12-21 2019-06-27 Daimler Ag Ventiltrieb für eine Verbrennungskraftmaschine, insbesondere eines Kraftfahrzeugs
CN108457714A (zh) * 2018-03-17 2018-08-28 潍柴重机股份有限公司 一种摇臂安装结构
DE102018008235B4 (de) * 2018-10-18 2020-11-26 Daimler Ag Ventiltrieb für eine Verbrennungskraftmaschine eines Kraftfahrzeugs, sowie Verfahren zum Betreiben eines solchen Ventiltriebs
DE102018132857A1 (de) * 2018-12-19 2020-06-25 Man Truck & Bus Se Schaltbare Betätigungsvorrichtung für ein Hubventil einer Brennkraftmaschine, Brennkraftmaschine und Kraftfahrzeug
GB2593916A (en) * 2020-04-09 2021-10-13 Daimler Ag Engine brake device for an engine of a vehicle
WO2022152581A1 (fr) * 2021-01-15 2022-07-21 Eaton Intelligent Power Limited Levier de vitesses à galets, ensemble barre de manoeuvre, ensemble galet de levier de vitesses, et galet de levier de vitesses pour actionnement de soupape variable dans un dispositif de distribution à soupape
CN113187578B (zh) * 2021-05-31 2022-05-13 宁波东方动力部件有限公司 一种内燃机缸内制动装置

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AU611323B2 (en) * 1986-05-21 1991-06-06 Coherent Automotive Technology Pty. Ltd. Improvements in engines for use with gaseous fuels
IT1255447B (it) * 1991-11-08 1995-10-31 Iveco Fiat Motore provvisto di un dispositivo di frenatura continua, particolarmente per un veicolo industriale.
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Also Published As

Publication number Publication date
JP6225258B2 (ja) 2017-11-01
US9874123B2 (en) 2018-01-23
WO2015070949A1 (fr) 2015-05-21
DE102013019000A1 (de) 2015-05-13
CN105723055B (zh) 2018-06-29
EP3068982B1 (fr) 2017-05-03
US20160298508A1 (en) 2016-10-13
JP2016537556A (ja) 2016-12-01
CN105723055A (zh) 2016-06-29

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