WO2012174697A1 - Dispositif de frein à culbuteur composite du type à chaîne fixe - Google Patents

Dispositif de frein à culbuteur composite du type à chaîne fixe Download PDF

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Publication number
WO2012174697A1
WO2012174697A1 PCT/CN2011/002186 CN2011002186W WO2012174697A1 WO 2012174697 A1 WO2012174697 A1 WO 2012174697A1 CN 2011002186 W CN2011002186 W CN 2011002186W WO 2012174697 A1 WO2012174697 A1 WO 2012174697A1
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WO
WIPO (PCT)
Prior art keywords
brake
rocker arm
engine
valve
toggle
Prior art date
Application number
PCT/CN2011/002186
Other languages
English (en)
Chinese (zh)
Inventor
柯恩九
柯即
杨洲
Original Assignee
上海尤顺汽车部件有限公司
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 上海尤顺汽车部件有限公司 filed Critical 上海尤顺汽车部件有限公司
Publication of WO2012174697A1 publication Critical patent/WO2012174697A1/fr

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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
    • 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
    • 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
    • F01L2001/186—Split rocking arms, e.g. rocker arms having two articulated parts and means for varying the relative position of these parts or for selectively connecting the parts to move in unison
    • 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
    • F01L2800/10—Providing exhaust gas recirculation [EGR]

Definitions

  • the present invention relates to the field of machinery, and more particularly to the field of valve actuation of vehicle engines, and more particularly to a technique for converting the normal operation of an engine into a brake operation of an engine, and more particularly to a solid-chain compound rocker arm brake device.
  • Engine braking technology is well known in the art.
  • Engine braking can be achieved by temporarily converting the engine to a compressor. The fuel is cut off during the conversion process, and the exhaust valve is opened at the end of the compression stroke of the engine piston, allowing the compressed gas (air during braking) to be released, and the energy absorbed by the compressed gas during the compression stroke of the engine cannot be subsequently expanded. The stroke returns to the engine piston, but is dissipated through the engine's exhaust and heat dissipation system. The end result is effective engine braking that slows down the speed of the vehicle.
  • a precedent for engine brakes is the hydraulic engine brake disclosed by Cummins, 1965, U.S. Patent No. 3,220,392.
  • the engine brakes in this technology pass the mechanical input through the hydraulic circuit to the exhaust valve to be opened.
  • the hydraulic circuit typically includes a primary piston that reciprocates within the primary piston bore from a mechanical input of the engine, such as movement of the engine fuel injection cam or movement of an adjacent exhaust cam.
  • the movement of the main piston is transmitted to the secondary piston on the hydraulic circuit through the hydraulic fluid to reciprocate in the secondary piston bore, and the secondary piston acts directly or indirectly on the exhaust valve to generate valve movement of the engine brake operation.
  • Cummins' engine brakes are accessories that are placed overhead on the engine.
  • a gasket is added between the cylinder and the bonnet, thus additionally increasing the height, weight and cost of the engine. It is clear that the solution to the above problem is to integrate the components of the brake device into existing components of the engine, such as integrated into the rocker arm of the engine, to form an integrated brake.
  • An integrated rocker brake system for an overhead cam type four-valve engine is disclosed in Volvo, Sweden, in U.S. Patent No. 5,564,385.
  • the brake system is very similar in structure and principle to the integrated rocker brake disclosed by JVS in 1974 under the patent No. 3, 809, 033.
  • the hydraulic brake piston is placed in a rocker cylinder near one end of the valve bridge and is movable between a non-braking position and a braking position to form a gap inside the engine valve train.
  • the pressurized oil is supplied to the brake piston through the pressure control valve to fill the valve gap in the rocker arm to form a hydraulic link.
  • the engine brake system adopts a combination mechanism of "funnel-shaped plunger valve + one-way ball width", which adds an overload relief mechanism and a fuel supply mechanism that uses a single oil passage to provide double oil pressure.
  • Double oil Low oil pressure (below the engine's oil pressure) Used for engine lubrication, double oil pressure high oil pressure (equal to engine oil pressure) for engine braking.
  • the brake piston pushes the valve bridge and simultaneously opens the two exhaust valve brakes.
  • a device that uses a double rocker to open a single valve brake is disclosed in US Pat. No. 7,392,772, to J.K., J.J., J.J. .
  • a dedicated brake rocker is added to its side.
  • Brake pistons and brake control valves have been added to the conventional exhaust rocker arm.
  • the special brake cam drives the special brake rocker arm, and the special brake rocker arm presses the brake piston.
  • the brake piston pushes the exhaust rocker arm and brakes an exhaust valve brake under the exhaust rocker arm.
  • the above-mentioned engine brake devices are hydraulically driven (also called hydraulic links) to transmit the engine brake load, the load components are deformed, the reliability is not ideal, and the weight and height of the engine are increased.
  • the object of the present invention is to provide a fixed-chain composite rocker arm brake device, which is characterized in that the engine brake device of the prior art is hydraulically driven and has a load element deformation. Increase technical weight and height of the engine.
  • the fixed-chain composite rocker brake device of the present invention includes a cam of an engine, and further includes a rocker An arm, a brake driving mechanism and a connecting mechanism, wherein the rocker arm is rotatably disposed on the rocker arm shaft, wherein the rocker arm is disposed between the cam and the valve of the engine, and the connecting mechanism Between the rocker arm and the valve of the engine, the connecting mechanism has a first position and a second position with respect to the rocker arm, and a gap is disposed between the first position and the second position, and the braking drive mechanism includes a a non-operating position and an operating position, wherein the brake drive mechanism and the coupling mechanism in the second position form a rigid mechanical link between the cam and the valve, the movement of the cam passing through A rigid mechanical link is transmitted to the valve to produce an engine braking operation. In the inoperative position, the brake drive mechanism releases the rigid mechanical link between the cam and the valve, and the brake drive mechanism is separated from the normal operation of the engine.
  • the method further includes at least one valve gap adjusting mechanism, wherein the valve gap adjusting mechanism adjusts a brake gap formed by the inoperative position and the operating position of the brake driving mechanism and the first position and the second position of the connecting mechanism Valve clearance.
  • the connecting mechanism includes a connecting member, and the connecting member is connected to the rocker arm through a rotating pair.
  • the connecting member is provided with a cylindrical hole, the cylindrical hole and the rocker arm shaft constitute a rotating pair, or a rocking arm is fixedly provided with a cylindrical pin, the cylindrical hole and the cylindrical body The pin constitutes a rotating pair.
  • rocker arm and the connecting member are alternately arranged on the same rocker arm shaft. Further, the brake driving mechanism is integrated in the rocker arm.
  • the brake drive mechanism is integrated within the connection mechanism.
  • the brake driving mechanism is a fixed-chain bearing mechanism
  • the fixed-chain carrier mechanism forms a mechanical link between the cam and the valve.
  • the fixed-chain bearing mechanism is a toggle mechanism of a single toggle lever
  • the toggle mechanism of the single toggle includes a toggle lever, a lock lever piston and a brake piston.
  • the moving piston includes a retracted position and an extended position. In the retracted position of the brake piston, the toggle lever is in an inclined state, and the toggle mechanism is in a loose non-operating position, and the extension of the brake piston In position, the toggle lever is in a straightened position and the toggle mechanism is in the locked operating position.
  • the fixed-chain bearing mechanism is a toggle mechanism of a double toggle
  • the toggle mechanism of the double toggle includes two toggles, two lock pistons and a brake piston.
  • the brake piston includes a retracted position and an extended position. In the retracted position of the brake piston, the two toggle levers are tilted, the toggle mechanism is in a slack, non-operating position, and the extension of the brake piston In the out position, the two toggle levers are in a straightened state, and the toggle mechanism is in the locked operating position.
  • the fixed-chain composite rocker arm braking device further includes a pre-tensioning spring, and the pre-tensioning spring maintains a gap formed by the first position and the second position of the connecting mechanism.
  • the working principle of the invention is: When the engine braking is required, that is, when the engine needs to be switched from the normal working state to the engine braking state, the brake control mechanism of the engine is turned on to supply oil to the brake driving mechanism, and the braking drive mechanism is The non-operating position becomes an operating position, eliminating a gap formed by the brake driving mechanism in the exhaust valve driving chain of the engine, and forming a link between the cam and the valve through the connecting member, transmitting the motion of the cam to the valve, and generating Engine braking.
  • the brake control mechanism of the engine When the engine brake is not required, the brake control mechanism of the engine is turned off, the brake drive mechanism is unloaded, and the brake drive mechanism is changed from the operating position to the non-operating position, forming a gap in the exhaust valve drive chain of the engine, and The normal operation of the engine is separated.
  • the effect of the present invention is positive and significant compared to the prior art.
  • the invention integrates the engine brake driving mechanism into the rocker arm or the connecting member, reduces the weight and height of the engine, expands the application range of the engine braking device, and uses the rigid mechanical link to carry the engine braking load, thereby improving the engine's Braking performance.
  • Figure 1 is a schematic view showing the first embodiment of the fixed-chain compound rocker arm brake device of the present invention in an "off" position of the engine brake device.
  • Fig. 2 is a schematic view showing the first embodiment of the fixed-chain compound rocker arm brake device of the present invention in the "open" position of the engine brake device.
  • Figure 3 is a diagram showing the brake control mechanism of the fixed-chain composite rocker arm brake device of the present invention being "on" Schematic of the location.
  • Fig. 4 is a view showing the brake control mechanism of the fixed-chain compound rocker arm brake device of the present invention in the "OFF" position.
  • Fig. 5 is a schematic view showing a cam profile of the fixed-chain composite rocker arm brake device of the present invention.
  • Fig. 6 is a view showing the second embodiment of the fixed-chain compound rocker arm brake device of the present invention in the "off" position of the engine brake device.
  • Fig. 7 is a view showing the third embodiment of the fixed-chain compound rocker arm brake device of the present invention in the "off" position of the engine brake device.
  • Fig. 8 is a view showing the fourth embodiment of the fixed-chain compound rocker arm brake device of the present invention in the "off" position of the engine brake device.
  • Fig. 9 is a view showing the fifth embodiment of the fixed-chain compound rocker arm brake device of the present invention in the "off" position of the engine brake device.
  • the fixed-chain composite rocker brake device of the present invention includes three main components: an exhaust valve actuator 200, an exhaust valve mechanism 300, and an engine brake drive mechanism 100.
  • the exhaust valve actuator 200 and the exhaust valve mechanism 300 are collectively referred to as an exhaust valve drive train.
  • the exhaust valve actuator 200 has many components including a cam 230, a cam follower 235 and a rocker arm 210.
  • the exhaust valve 301 (which may also be a dual exhaust valve) of the exhaust valve mechanism 300 is biased by the valve spring 310 of the engine on the valve seat 320 of the engine block 500 to prevent gas between the engine cylinder and the exhaust pipe 600. flow.
  • the exhaust valve actuator 200 also includes other components, such as a valve clearance adjustment mechanism and a foot pad 114.
  • the valve clearance adjusting mechanism of the present invention is not directly mounted on the rocker arm 210, but is coupled to the rocker arm 210 by a rotating pair formed by the cylindrical pin 284 of the coupling mechanism 250 and the cylindrical hole 282.
  • valve clearance adjusting screw 1 10 is locked to the connecting mechanism by the nut 105 250 connector 280.
  • the rocker arm 210 is rockingly mounted on the rocker shaft 205, and the movement of the cam 230 is transmitted to the exhaust valve 301 through the connecting member 280, the wide gap adjusting mechanism and the foot pad 1 14, so that it is periodically opened and closed. .
  • the cam 230 integrates the dual function of the engine's conventional exhaust and brake.
  • the inner base circle 225 of the cam 230 has an enlarged boss 220 which is mainly used for the conventional exhaust operation of the engine.
  • the enlarged boss 220 is larger than the conventional (without engine brake) exhaust boss, and is also called integration. Exhaust boss.
  • the reason for the increase is that the cam 230 also has a brake boss (small boss 232 and small boss 233) for engine braking.
  • the bottom of the enlarged boss 220 In the normal (ignition) operation of the engine, in order to skip the brake boss (small boss 232 and small boss 233), the bottom of the enlarged boss 220 must be added with the brake boss (small boss 232 and small convex) Stage 233) is approximately the same transition section, and its top corresponds to a conventional exhaust boss.
  • the small boss 232 is used for exhaust gas recirculation during braking, and the small boss 233 is used for compression release during braking.
  • the brake drive mechanism 100 includes a fixed chain load-bearing mechanism integrated in the rocker arm 210, as shown in Figures 1 and 2, with a toggle mechanism.
  • the toggle mechanism with double toggles includes toggle 184 and toggle 186, lock piston 162 and lock piston 164, and a brake piston 160.
  • the return spring 156 urges the lock bar piston 162 and the lock bar piston 164 to bias the toggle lever 184 and the toggle lever 186 in an inclined position, and the brake piston 160 is in the rocker arm 210.
  • the retracted position forms a brake gap 130 with the connector 280.
  • the retracted position and the extended position of the brake piston 160 not only directly generate the brake gap 130, but also indirectly create the valve clearance 234.
  • the valve clearance 234 is located between the rocker arm 210 and the connector 280 of the coupling mechanism 250 and is slightly smaller than the brake gap 130.
  • the brake gap 130 is slightly larger than the stroke of the brake piston 160 between its retracted position and the extended position.
  • a pretension spring 198 between the connector 280 and the rocker arm 210 is used to maintain the valve clearance 234 to avoid non-following and sudden collisions between the connector 280 and the rocker arm 210.
  • the brake drive mechanism 100 in the inoperative position as shown in FIG. 1 is separated from the normal operation of the engine and does not receive any load. Nor does it pass any movement.
  • the brake control mechanism 50 When engine braking is required, as shown in FIG. 3, the brake control mechanism 50 is opened. Brake control The control valve 51 of the mechanism is coupled to the inlet of the axial oil passage 2 in the rocker shaft 205 and passes through other brake oil supply passages, such as the radial bore 212 in the rocker shaft 205, the slit 213 in the rocker arm 210, and The oil passage 214 supplies oil to the brake drive mechanism 100. The oil pressure overcomes the force of the return spring 156, pushing the lock rod piston 164 and the lock rod piston 162 upward, and the toggle rod 184 and the toggle rod 186 are changed from the inclined position to the extended position and locked (Fig.
  • the brake piston The 160 is in the extended position within the rocker arm 210 to release the brake gap 130 between the connector 280. That is, the brake drive mechanism 100 in the operating position shown in FIG. 2 forms a mechanical link between the cam 230 and the exhaust valve 301 via the connector mechanism 250, and moves the cam 230 through the valve clearance adjustment mechanism. And the foot pad 1 14, is transmitted to the exhaust valve 301 to generate the braking operation of the engine.
  • the brake control mechanism 50 When the engine brake is not required, as shown in FIG. 4, the brake control mechanism 50 is closed, and the valve body of the control valve 51 closes the oil supply port 1 11 and simultaneously opens the oil discharge port 222, and the brake drive mechanism 100 The brake fluid passage and the oil discharge port 222 are unloaded.
  • the lock rod piston 164 and the lock rod piston 162 of Figures 1 and 2 are pushed down by the return spring 156 without oil pressure, and the toggle rod 184 and the toggle rod 186 are biased as shown in Figure 1.
  • the brake piston 160 In the tilted position, the brake piston 160 is retracted to the non-braking position by the brake spring 177, and a brake gap 130 is formed with the connecting member 280.
  • the brake control mechanism 50 of the fixed-chain composite rocker brake device of the present invention is in the "on" and “off” positions.
  • the control valve 51 in the figure is a two-position three-way type solenoid valve.
  • the valve body of the control valve 51 opens the oil supply port 1 1 1 downward, and simultaneously closes the oil discharge port 222, and the low-pressure oil (lubricating oil) of the engine is from the brake fluid passage. Flows to the brake drive mechanism 100 (Figs. 1 and 2).
  • the brake control mechanism 50 is closed (Fig.
  • valve body of the control valve 51 closes the oil supply port 111 upward, while the oil discharge port 222 is slammed, and the low pressure oil (lubricating oil) of the engine stops flowing to the brake drive mechanism 100. (Figs. 1 and 2), the brake drive mechanism 100 unloads oil from the brake fluid passage and the oil discharge port 222.
  • Fig. 5 shows a cam profile in the fixed-chain composite rocker brake device of the present invention, which includes a brake boss and an integrated exhaust boss 220.
  • 225 is the inner base circle of the cam.
  • the brake boss includes a small boss 232 and a small boss 233.
  • the integrated exhaust boss 220 is divided into a bottom and a top (the two-dot chain line in Figure 5 separates them).
  • the bottom of the integrated exhaust boss 220 is a transition portion that is approximately the same height as the brake boss; the top of the integrated exhaust boss 220 is approximately the same as the conventional boss of the engine without the engine brake.
  • the engine brake device of the second embodiment of the fixed-chain compound rocker arm brake device of the present invention is in the "OFF" position. Only a portion of the brake drive mechanism 100 is shown in FIG. 6, which is a toggle mechanism with a single toggle, including a toggle lever 186, a lock bar piston 162, and a brake piston 160.
  • FIG. 6 is a toggle mechanism with a single toggle, including a toggle lever 186, a lock bar piston 162, and a brake piston 160.
  • the return spring 156 will lock the lever The piston 162 is pushed down so that the toggle lever 186 is in the tilted position, the brake piston 160 is in the corresponding retracted position, and the toggle mechanism is in the inoperative position without locking.
  • Spring 156 is secured to rocker arm 210 by spring seat 158 and snap ring 157.
  • the brake control mechanism 50 When engine braking is required, as shown in Fig. 3, the brake control mechanism 50 is opened, and the brake drive mechanism 100 of Fig. 6 is supplied with oil through an oil supply passage including an oil passage 214 in the rocker arm 210.
  • the oil pressure overcomes the urging force of the return spring 156, pushes the lock rod piston 162 upward, causes the toggle lever 186 to change from the inclined position to the extended position, and locks, and the brake piston 160 changes from the retracted position to the extended position in the rocker arm 210.
  • a mechanical link is formed between the cam 230 and the exhaust valve 301 as shown in FIGS. 1 and 2, and the movement of the cam 230 is transmitted to the exhaust valve 301 through the valve gap adjusting mechanism and the foot pad 114. Produce the brake operation of the engine.
  • the engine brake device of the third embodiment of the fixed-chain compound rocker arm brake device of the present invention is in the "OFF" position.
  • the valve clearance adjusting mechanism of the exhaust valve of this embodiment is directly disposed on the rocker arm 210.
  • the valve clearance adjusting screw 110 which is locked to the rocker arm 210 by the nut 105, adjusts the valve clearance 234 between it and the pressure ball 112.
  • the pressure ball 112 can slide up and down within the hole of the adjustment screw.
  • the underside of the pressure bar 112 is coupled to the foot pad 114 and is coupled to the connector 280 of the attachment mechanism 250.
  • the coupling mechanism 250 also includes a cylindrical pin 284 and a rotating pair formed by the cylindrical bore 282.
  • the brake valve clearance adjusting mechanism is also added in this embodiment, and the valve clearance adjusting screw 1102 locked by the nut 1052 on the rocker arm 210 can adjust between the brake piston 160 and the connecting member 180. Brake gap 130. Additionally, a pretension spring 198 that maintains the valve clearance 234 is located between the adjustment screw 110 (rocker arm 210) and the foot pad 114.
  • the brake control mechanism 50 When engine braking is required, as shown in Fig. 3, the brake control mechanism 50 is opened, and the brake drive mechanism 100 of Fig. 7 is supplied with oil through an oil supply passage including an oil passage 214 in the rocker arm 210.
  • the oil pressure overcomes the force of the return spring 156, pushing the lock rod piston 164 and the lock rod piston 162 upward, so that the toggle rod 184 and the toggle rod 186 are changed from the inclined position to the extended position and locked, and the brake piston 160 is on the rocker arm.
  • the 210 is in the extended position to substantially release the brake gap 130 between the connector 280.
  • the brake drive mechanism 100 in the operating position forms a mechanical link between the cam 230 and the exhaust valve 301 via the connector mechanism 250, transmitting the motion of the cam 230 to the exhaust valve 301, generating brakes of the engine. Operation.
  • the brake control mechanism 50 When the engine brake is not required, as shown in Fig. 4, the brake control mechanism 50 is turned off to unload the oil.
  • the lock lever piston 164 and the lock rod piston 162 of FIG. 7 are pushed down by the return spring 156 without oil pressure, and the toggle lever 184 and the toggle lever 186 are biased at the inclined position as shown in FIG.
  • the brake piston 160 is retracted to the non-braking position by the brake spring 177, and a brake gap 130 is formed with the connecting member 280.
  • the mechanical linkage formed by the brake drive mechanism 100 between the cam 230 and the exhaust valve 301 via the connector 280 is switched or released.
  • the brake piston 160 in the brake drive mechanism 100 and the connector 280 in the coupling mechanism are not subjected to any load and do not transmit any movement.
  • the brake drive mechanism 100 is separated from the normal operation of the engine.
  • the engine brake device of the fourth embodiment of the fixed-chain compound rocker arm brake device of the present invention is in the "OFF" position.
  • the only difference between this embodiment and the third embodiment described above is the position of the brake drive mechanism within the rocker arm 210, which works in exactly the same way.
  • the fifth embodiment of the fixed-chain composite rocker arm brake device of the present invention differs from the first embodiment in the following structure: 1.
  • the rocker arm 210 is a "semi-rocker arm" disposed above the rocker shaft 205;
  • the connecting member 280 of the connecting mechanism 250 is another "semi-rocker arm" disposed on the rocker shaft 20.5, so the “cylinder pin” of the rotating pair of the connecting mechanism 250 is the rocker shaft 205;
  • the toggle mechanism of the brake drive mechanism 100 with double toggles is integrated in the connector 280.
  • the working principle of this embodiment is the same as that of the first embodiment, and will not be repeated here.
  • solid-chain composite rocker braking method and apparatus shown herein is applicable to both overhead cam and pusher engines as well as single-valve engines and dual-valve engines.
  • a single-valve brake or a dual-valve brake can be used.
  • the brake drive mechanism 100 may be either a solid chain type or a hydraulic type.
  • the position and orientation or arrangement of the brake drive mechanism 100 can also be varied.
  • the rocker arm 210 can also be a dedicated brake rocker arm.
  • brake cams herein may be dedicated brake cams, injection cams, and exhaust cams. Therefore, the scope of the invention should not be determined by the specific examples described above, but by the appended claims and their legal equivalents.

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

Abstract

Un dispositif de frein à culbuteur composite du type à chaîne fixe comprend une came (230) d'un moteur, un culbuteur (210), un mécanisme d'entraînement de frein (100) et un mécanisme de liaison (250). Le culbuteur est installé rotatif sur un arbre (205) de culbuteur, le culbuteur est disposé entre la came et un clapet (301) du moteur, et le mécanisme de liaison est disposé entre le culbuteur et le clapet du moteur. Le mécanisme de liaison est doté d'une première position et d'une seconde position par rapport au culbuteur, et il existe un espace entre la première position et la seconde position. Le mécanisme d'entraînement de frein est doté d'une position de non-fonctionnement et d'une position de fonctionnement. Dans la position de fonctionnement, le mécanisme d'entraînement de frein forme une liaison mécanique solide entre la came et le clapet tandis que le mécanisme de liaison se trouve dans la seconde position, le mouvement de la came est transmis au clapet par l'intermédiaire de la liaison mécanique solide et une opération de freinage du moteur est produite. Dans la position de non-fonctionnement, le mécanisme d'entraînement de frein supprime la liaison mécanique solide entre la came et le clapet, et le mécanisme d'entraînement de frein se désolidarise du fonctionnement normal du moteur. L'incorporation du mécanisme d'entraînement de frein du moteur dans le culbuteur du dispositif de frein permet de réduire le poids et la hauteur du moteur et d'améliorer les performances de freinage du moteur.
PCT/CN2011/002186 2011-06-24 2011-12-26 Dispositif de frein à culbuteur composite du type à chaîne fixe WO2012174697A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201110172628.6 2011-06-24
CN201110172628.6A CN102840005B (zh) 2011-06-24 2011-06-24 一种固链式复合摇臂制动装置

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WO2012174697A1 true WO2012174697A1 (fr) 2012-12-27

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WO2015022071A1 (fr) * 2013-08-12 2015-02-19 Avl List Gmbh Dispositif d'actionnement de soupape permettant de modifier la course de soupape
WO2016040019A1 (fr) * 2014-09-09 2016-03-17 Caterpillar Inc. Procédé de refabrication d'un bras de culbuteur et bras de culbuteur refabriqué
DE102017205814A1 (de) * 2017-04-05 2018-10-11 Avl List Gmbh Mechanische Ventilbetätigungsvorrichtung
EP4018081A4 (fr) * 2019-08-19 2024-02-14 Shanghai Universoon Autotech Co., Ltd. Appareil d'actionnement de soupape de moteur

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CN104279020B (zh) * 2013-07-10 2017-11-24 上海尤顺汽车部件有限公司 一种固链式发动机气门驱动装置
CN104712397B (zh) * 2015-03-05 2020-08-25 上海尤顺汽车部件有限公司 一种复合摇臂发动机制动装置
US10690024B2 (en) 2015-01-21 2020-06-23 Eaton Corporation Rocker arm assembly for engine braking
WO2016118548A1 (fr) 2015-01-21 2016-07-28 Eaton Corporation Ensemble culbuteur pour freinage de moteur
US11092042B2 (en) 2015-01-21 2021-08-17 Eaton Intelligent Power Limited Rocker arm assembly with valve bridge
JP6887440B2 (ja) 2016-03-16 2021-06-16 イートン インテリジェント パワー リミテッドＥａｔｏｎ Ｉｎｔｅｌｌｉｇｅｎｔ Ｐｏｗｅｒ Ｌｉｍｉｔｅｄ ロッカアームアセンブリ
TR201720332A2 (tr) * 2017-12-14 2019-07-22 Ford Otomotiv Sanayi As Bi̇r külbütör mekani̇zmasi
WO2019127188A1 (fr) * 2017-12-28 2019-07-04 潍柴动力股份有限公司 Ensemble culbuteur de soupape, mécanisme de distribution d'air variable et moteur
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
WO2022218114A1 (fr) * 2021-04-14 2022-10-20 上海尤顺汽车技术有限公司 Système de freinage à quatre temps de moteur, procédé et système de levée de soupape de freinage de moteur
CN113482737A (zh) * 2021-08-24 2021-10-08 庄辉 一种发动机的气门驱动装置及其驱动方法

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