• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    mounting of primary and auxiliary swing arms for actuating the engine valve. systems and methods for actuating engine valves are revealed. systems may include primary and auxiliary swing arms disposed adjacent to each other on a swing arm axis. the primary swingarm can actuate engine valves for primary valve actuation movements, such as main exhaust events, in response to an input from a first valve train element, such as a cam. the auxiliary swingarm may receive one or more auxiliary valve actuation movements, such as for engine braking events, exhaust gas recirculation and/or brake gas recirculation, from a second valve train element to actuate one of the engine valves. master and slave pistons can be provided on the primary swingarm. the master piston can be actuated by the auxiliary swingarm.
    公开号:BR112013029941B1
    申请号:R112013029941-0
    申请日:2012-05-25
    公开日:2021-06-01
    发明作者:Robb Janak；Brian Ruggiero；Zdenek S. Meistrick
    申请人:Jacobs Vehicle Systems, Inc.；
    IPC主号:
    专利说明:

    CROSS REFERENCE TO RELATED ORDERS
    [001] This application concerns and claims the benefit of the earlier filing date and priority of provisional patent application US 61/490,544, filed May 26, 2011, and entitled "Primary And Half Rocker Arm Assembly For Engine Valve Actuation ”. FIELD OF THE INVENTION
    [002] The present invention relates to systems and methods to activate trigger valves in internal combustion engines. BACKGROUND OF THE INVENTION
    [003] Internal combustion engines typically use a mechanical, electrical or hydromechanical valve drive system to drive the engine valves. These systems can include a combination of camshafts, swing arms and push rods that are driven by the engine's crankshaft rotation. When a camshaft is used to drive the engine valves, the timing of the valve drive can be fixed by the size and location of the lobes on the camshaft.
    [004] For each 360 degree rotation of the camshaft, the engine completes a complete cycle consisting of four strokes (ie, expansion, exhaust, intake and compression). Both the intake and exhaust valves can be closed, and remain closed, during most of the expansion stroke where the piston is being moved away from the cylinder head (i.e., the volume between the cylinder head and the piston head is increasing). During positive power operation, fuel is burned during the expansion stroke and positive power is delivered by the engine. The expansion stroke ends at bottom dead center, at which time the piston reverses direction and the exhaust valve can be opened for a main exhaust event. A lobe on the camshaft can be timed to open the exhaust valve to the main exhaust event as the piston is moved upward and forces the flue gases out of the cylinder. Near the end of the exhaust stroke, another lobe on the camshaft can open the intake valve for the main intake event at which time the piston is moved away from the cylinder head. The inlet valve is closed and the inlet stroke ends when the piston is near bottom dead center. Both the intake and exhaust valves are closed as the piston is moved back up to the compression stroke.
    [005] The main inlet and main exhaust valve events referenced above are required for positive power operation of an internal combustion engine. Additional auxiliary valve events, although not required, may be desirable. For example, it may be desirable to actuate the intake and/or exhaust valves during positive power or other engine operating modes for compression release engine braking, bleed engine braking, exhaust gas recirculation (EGR), brake gas recirculation (BGR), or other auxiliary inlet and/or exhaust valve events. Figure 5 illustrates examples of a main exhaust event 600 and auxiliary valve events, such as a compression release engine brake event 610, the bleed engine brake event 620, the exhaust gas recirculation event 640 and brake gas recirculation event 630, which can be performed by an engine valve using various embodiments of the present invention to trigger engine valves for main and auxiliary valve events.
    [006] With respect to auxiliary valve events, exhaust gas flow control through an internal combustion engine has been used in order to provide vehicle engine braking. Generally speaking, engine braking systems can control the exhaust gas flow to incorporate the principles of compression release type braking, exhaust gas recirculation, exhaust pressure regulation and/or bleed type braking .
    [007] During compression release-type engine braking, the exhaust valves can be selectively opened to convert, at least temporarily, an internal combustion engine producing power into an air compressor absorbing power. As a piston is moved upwards during its compression stroke, gases that are trapped in the cylinder can be compressed. Compressed gases can oppose the upward movement of the piston. As the piston approaches the top dead center (TDC) position, at least one exhaust valve can be opened to release the compressed gases in the cylinder to the exhaust manifold, preventing the energy stored in the compressed gases from being returned to the engine on the descending stroke of subsequent expansion. In doing so, the engine can develop retarding power to help slow the vehicle down. An example of a prior art compression release motor brake is provided by Cummins disclosure, US Patent 3,220,392 (November 1965), which is incorporated herein by reference.
    [008] During bleed-type engine braking, in addition to and/or in place of the main exhaust valve event, which occurs during the piston exhaust stroke, the exhaust valve(s) may be kept slightly open for the remaining three engine cycles (full-cycle bleed brake) or for a portion of the remaining three engine cycles (partial-cycle bleed brake). Bleeding cylinder gases into and out of the cylinder can act to slow down the engine. Usually, the initial opening of the brake valve(s) in a bleed brake operation is in advance of the compression TDC (ie before valve actuation) and then lift is held constant for a period of time. As such, a bleed-type engine brake may require less force to actuate the valve(s) because of earlier valve actuation, and may generate less noise because of continuous bleeding rather than the rapid discharge of a compression release type brake.
    [009] Exhaust gas recirculation (EGR) systems may allow a portion of the exhaust gases to flow back into the engine cylinder during positive power operation. EGR can be used to reduce the amount of NOx created by the engine during positive power operations. An EGR system can also be used to control the pressure and temperature in the exhaust manifold and engine cylinder during engine braking cycles. Generally speaking, there are two types of EGR systems, internal and external. External EGR systems recirculate exhaust gases back to the engine cylinder through an intake valve(s). Internal EGR systems recirculate exhaust gases back to the engine cylinder through an exhaust valve(s) and/or an inlet valve(s). Embodiments of the present invention relate primarily to in-house EGR systems.
    [010] Brake gas recirculation (BGR) systems may allow a portion of the exhaust gases to flow back into the engine cylinder during engine braking operation. Recirculation of exhaust gases back to the engine cylinder during the intake stroke, for example, can increase the mass of gases in the cylinder that are available for compression release braking. As a result, BGR can increase the braking effect achieved by the braking event. SUMMARY OF THE INVENTION
    [011] Responsive to the challenges mentioned above, the applicants have developed an innovative system to actuate first and second engine valves associated with the same engine cylinder, comprising: an axle of swing arms; a device for transmitting primary valve actuating motion; a primary rocker arm disposed on the rocker arm shaft, said primary rocker arm being adapted to drive the first and second engine valves and to receive motion from the device for transmitting primary valve driving motion; a device for transmitting auxiliary valve actuating motion; an auxiliary swing arm disposed adjacent the primary swing arm, said auxiliary swing arm being adapted to receive movement from the device to transmit auxiliary valve actuating motion; a master piston disposed in a master piston bore in the primary swingarm; a slave piston disposed in a slave piston hole in the primary swingarm, said slave piston positioned to provide auxiliary valve actuating motion only to the first of the first and second engine valves; a control valve disposed in a control valve hole in the primary swingarm; and a hydraulic circuit connecting the master piston hole, slave piston hole and control valve hole.
    [012] Applicants have further developed an innovative system for actuating first and second engine valves comprising: a swing arm axle; a primary swingarm disposed on the swingarm axis, said primary swingarm having a master piston boss extending laterally from a main body of the primary swingarm; an auxiliary swingarm disposed adjacent to the primary swingarm main body on one side of the primary swingarm from which the master piston boss extends; a master piston disposed in a master piston hole in the boss for the master piston; a slave piston disposed in a slave piston hole in the main body of the primary swingarm; a valve bridge extending between the first and second engine valves, and having a center surface adapted to contact the primary swingarm drive end, said valve bridge additionally having a side opening extending through a first end of the valve bridge above the first engine valve; a slide pin disposed in the valve bridge side opening and extending between and contacting the first engine valve and the slave piston; and a hydraulic circuit connecting the master piston hole, slave piston hole and a source of hydraulic fluid.
    [013] Applicants have also further developed an innovative method of actuating first and second engine valves for primary and auxiliary valve actuation events using a primary swing arm, an auxiliary swing arm mounted adjacent to the primary swing arm, and a motion system master-slave hydraulic lost incorporated into the primary swingarm, said method comprising the steps of: actuating the first and second engine valves to a primary valve actuation event responsive to motion transmitted from a first valve train element to the primary swingarm during an engine operating primary valve actuation mode; apply hydraulic fluid to the master-slave hydraulic lost motion system to extend master and slave pistons from the primary swingarm during a time when an auxiliary valve actuation event is to be transmitted only to the first of the first and second valves. motor; and actuating only the first of the first and second engine valves for an auxiliary valve actuation event using the master-slave hydraulic lost motion system responsive to motion transmitted from a second valve train element to the auxiliary swingarm during an engine operation auxiliary valve actuation mode.
    [014] It is to be understood that both the above general description and the detailed description below are only exemplary and explanatory, and are not restrictive of the invention as claimed. BRIEF DESCRIPTION OF THE DRAWINGS
    [015] In order to aid in the understanding of this invention, reference will now be made to the accompanying drawings, in which like reference numerals refer to like elements.
    [016] Figure 1 is a top plan view of a master and slave swingarm system and auxiliary swingarm assembled according to a first embodiment of the present invention.
    [017] Figure 2 is a partial cross-section of the embodiment of the present invention shown in Figure 1 taken along section line A-A.
    [018] Figure 3 is a partial cross-section of the embodiment of the present invention shown in Figure 1 taken along section line B-B.
    [019] Figure 4 is an enlarged view of the hydraulic control valve and slave piston circuit in the master and slave swingarm shown in figure 1.
    [020] Figure 5 is a graph of several different and exemplary auxiliary valve events. DETAILED DESCRIPTION OF MODALITIES OF THE INVENTION
    [021] Reference will now be made in detail to a first embodiment of the present invention, an example of which is illustrated in the attached drawings. With reference to figure 1, a system for actuating engine valves is shown. Figure 1 is a top view of a primary swingarm 100 which may be referred to as an exhaust swingarm herein, but which is not limited to being an exhaust swingarm. An auxiliary (or offset) swing arm 200 is mounted adjacent to the primary swing arm 100. Figure 2 is a partial cross-sectional side view of the exhaust swing arm 100 taken along section line AA in Figure 1. Figure 3 is a partial cross-sectional side view of auxiliary rocker arm 200 taken along section line BB in figure 1. Referring to figures 1-3, referenced engine valves 400 are tailstock type valves that are used for control communication between combustion chambers (eg cylinders) in an engine and suction manifolds (eg intake and exhaust). The system includes a swing arm shaft 500 on which the primary and auxiliary swing arms 100 and 200 can be disposed. In an alternative embodiment, each of the primary and auxiliary swing arms 100 and 200 can be mounted on its own swing axle. The primary and auxiliary swing arms 100 and 200 may be articulated around the swing arm shaft 500 as a result of motion transmitted to them by a camshaft 300 or some other device to impart motion.
    [022] When the primary swingarm 100 is an exhaust swingarm, both it and the auxiliary swingarm 200 can be adapted to actuate engine valves, such as an exhaust valve 400, by contacting them directly (not shown) or via a valve bridge 450 (shown). In such a case, the auxiliary swingarm 200 is adapted to selectively actuate at least one exhaust valve 400 by contacting a master piston 114 provided in the exhaust swingarm 100 which is in hydraulic communication with a slave piston 172 in the exhaust swingarm, and which in turn acts on a single exhaust valve of a set of two or more exhaust valves associated with the same engine cylinder by means of a slide pin 460.
    [023] The swing arm shaft 500 may include one or more internal passages for delivering hydraulic fluid, such as engine oil, to the swing arms mounted thereon. Specifically, the swing arm shaft 500 may include a control fluid supply passage 520. The control fluid supply passage 520 may supply hydraulic fluid to the master and slave hydraulic circuit in the exhaust swing arm 100 by means of an oscillating shaft passage 510. A solenoid control valve (not shown) can control the supply of low pressure hydraulic fluid to the control fluid supply passage 520.
    [024] Referring to both Figures 1 and 2, the exhaust swing arm 100 includes a swing shaft hole 104 extending laterally through a central portion of the swing arm. The rocker shaft hole 104 may be adapted to receive the rocker arm shaft 500. The rocker shaft hole 104 may include one or more ports formed in the wall thereof for receiving fluid from the control fluid supply passage 520 formed within the swing arm axle 500.
    [025] The exhaust swing arm 100 may include a valve drive end 106 having a thrust adjustment screw 108. The thrust adjustment screw 108 may protrude from the underside of the valve drive end 106 and allow adjustment of the thrust space between the valve drive end 106 of the exhaust swing arm and the exhaust valve bridge 450. The thrust adjustment screw can be locked in place by a nut. Optionally, a self-adjusting hydraulic thrust adjuster can be the replacement for the manually adjustable thrust adjustment screw, or thrust adjustment may not be provided at all.
    [026] Referring to Figures 1-3, a master piston boss 110 may extend laterally from the valve drive end 106 of the exhaust swing arm main body so that it is positioned below the valve drive end. valve 206 of auxiliary rocker arm 200. Figure 3 is a cross-sectional side view showing master piston boss 110. A master piston hole 112 may be formed in boss 110 and a master piston 114 may be slidably disposed. velable in master piston bore 112. A master piston retaining cup 116 may be located near the open end of master piston bore 112. Retaining cup 116 may have a central opening through which master piston 114 can be seated. extend. Retaining cup 116 can be prevented from sliding out of master piston hole 112 by a retaining washer. An optional spring 120 may extend between the retaining cup 116 and a shoulder provided in the master piston 114 so that the master piston is biased within the master piston hole 112. A fluid passage 164 can connect the master piston hole to a slave piston bore 170 or fluid passage 162.
    [027] Referring to Figures 1-4, the exhaust swingarm 100 may include a slave piston hole 170 adjacent to the master piston hole 112 and a slave piston 172 may be slidably disposed in the slave piston hole 170. A slave piston holding cup 174 may be located near the open end of the slave piston bore 170. The holding cup 174 may have a central opening through which the slave piston 172 may extend. Retaining cup 174 can be prevented from sliding out of slave piston bore 170 by a retaining washer. An optional spring 176 may extend between retaining cup 174 and a shoulder provided on slave piston 172 such that the slave piston is biased within slave piston bore 170. Fluid passageway 164 may connect slave piston bore 170 or passage 162 extending from slave piston hole to master piston hole 112.
    [028] A thrust adjusting screw 178 may extend through the exhaust swingarm 100 to contact the slave piston 172. The thrust adjusting screw 178 may protrude from the top of the valve drive end 106 of the swingarm. exhaust and allow adjustment of the thrust space between the lower end of the slave piston 172 and the slide pin 460 on the exhaust valve bridge 450. The thrust adjustment screw can be locked in place by a nut. Optionally, a self-adjusting hydraulic thrust adjuster can be the replacement for the manually adjustable thrust adjustment screw, or thrust adjustment may not be provided at all.
    [029] The exhaust swing arm 100 may also include a control valve bore 124 at the end of the swing arm proximal to the valve drive end 106. A control valve piston 130 may be disposed in a control valve bore 124. Control valve piston 130 can control the supply of hydraulic fluid to the master and slave hydraulic circuit which includes master and slave piston holes 112 and 170 and fluid passages 162 and 164. The control can be oriented vertically, as shown in figures 2 and 4, or in an alternative mode in some other orientation, such as horizontally.
    [030] Figure 4 shows the details of the control valve piston 130 used in the first embodiment of the present invention. The control valve piston 130 may be a cylindrical shaped element with one or more internal passages, and which may incorporate an internal control check valve 140. The check valve 140 may allow fluid to pass the fluid passage. control 160 for fluid supply passage 162, but not in the opposite direction. The control valve piston 130 may be spring biased by one or more control valve springs 133 in the control valve bore 124 to the lower portion 135 of the control valve bore. A central inner passage may extend axially from the inner end of the control valve piston 130 towards the middle of the control valve piston where the control check valve 140 may be located. The central internal passage in control valve piston 130 may communicate with one or more passages extending through the diameter of control valve piston 130. As a result of upward translation of control valve piston 130 relative to its bore 124, as shown in Figure 4, the passages extending through the control valve piston 130 can selectively align with a port that connects the side wall of the control valve bore with the second fluid passage 162. extending through the control valve piston 130 are aligned with the second fluid passage 162, low pressure fluid may flow from the first fluid passage 160, through the control valve piston 130 and into the second fluid passage 162 for filling the hydraulic circuit of master and slave.
    [031] The exhaust swing arm 100 may include one or more internal passages 160, 162 and 164 for delivering hydraulic fluid through the exhaust swing arm to fill the master and slave hydraulic circuit contained therein. A port at the end of the first fluid passage 160 may communicate with the swing shaft hole 104 and may align with the control fluid supply passage 520 provided on the swing arm shaft 500 when the exhaust swing arm is mounted on the swing arm axle. The first fluid passage 160 may extend between the swing shaft bore 104 and the control valve bore 124. The second fluid passage 162 may extend through the exhaust swing arm 100 from the control valve bore 124 to the slave piston hole 170. The third fluid passage 164 may extend from the master piston hole 112 to the slave piston hole 170 or to the second fluid passage 162. Taken together, the master piston, slave piston and the hydraulic circuit connecting them together can form a master-slave hydraulic lost motion system that is incorporated into the primary swingarm 100.
    [032] With renewed reference to figures 1 and 2, an exhaust swing cam roller 102 can be connected to the exhaust swing arm 100. The exhaust swing cam roller 102 can contact an exhaust cam 310 (i.e. , device for transmitting primary valve actuation) provided on camshaft 300. Exhaust cam 310 may include one or more lobes, including a lobe adapted to produce a primary valve opening event, such as a main exhaust event, transmitting a primary valve actuating motion to the exhaust swing arm 100. It is appreciated that the primary valve actuating motion can be transmitted to the exhaust swing arm 100 via any number of alternative valve train elements , including, but not limited to, cams, thrust tubes, swing arms, levers, hydraulic and electromechanical actuators, and more.
    [033] Referring to Figures 1 and 3, the auxiliary swingarm 200 includes a swing shaft hole 204 extending laterally through a central portion of the displaced swingarm. The rocker shaft hole 204 may be adapted to receive the rocker arm shaft 500. The auxiliary rocker arm 200 may additionally include a valve drive end 206 and a thrust adjusting screw 208. The thrust adjusting screw 208 may protrude from the bottom of the valve drive end 206 and allow adjustment of the thrust space between the valve drive end 206 of the auxiliary rocker arm and the master piston 114. The thrust adjustment screw 208 can be locked in place by a nut. Optionally, a hydraulic or other self-adjusting thrust adjuster can be the replacement for thrust adjustment screw 208.
    [034] An auxiliary swing cam roller 202 can be connected to the offset swing arm 200. The auxiliary swing cam roller 202 can contact an auxiliary cam 320 (ie, device to provide auxiliary valve drive) provided on camshaft 300 Referring to Figure 3 in particular, auxiliary cam 320 may include one or more cam lobes such as, for example, an engine braking cam lobe 330, an exhaust gas recirculation (EGR) cam lobe 340 and/or a brake gas recirculation (BGR) cam lobe 350 adapted to transmit one or more auxiliary valve actuating movements to the auxiliary swing arm 200. It is understood that these auxiliary valve actuating movements can be transmitted to the auxiliary drive swingarm 200 via any number of alternative valve train elements, including, but not limited to, cams, thrust tubes, swingarms, lever hydraulic and electromechanical actuators and more. The 330 engine braking cam lobe can be adapted to provide compression release, bleed or partial bleed engine braking. Compression release engine braking involves opening an exhaust valve (or an auxiliary engine valve) near the top dead center position for the engine piston in compression strokes (and/or exhaust strokes for two-cycle braking) for the piston. Bleed engine braking involves opening an exhaust valve for the complete engine cycle; and partial bleed engine braking involves opening an exhaust valve for a significant portion of the engine cycle. The optional EGR lobe can be used to provide an EGR event during a positive power mode of engine operation. The optional BGR lobe can be used to provide a BGR event during a motor-operating motor brake mode. The valve actuating movements provided by motor brake lobe 330, EGR lobe 340 and BGR lobe 350 are intended to be examples of auxiliary valve actuating movements that may be provided by auxiliary swing arm 200.
    [035] Referring to Figure 1, a mousetrap-type spring 210 can engage the auxiliary swingarm 200 and the swing shaft 500. As shown, the spring 210 can bias the auxiliary swing arm 200 in the direction of the camshaft 300 Spring 210 may have sufficient strength to keep auxiliary swingarm 200 in contact with auxiliary cam 320 through the entire rotation of the camshaft. In an alternative embodiment, spring 210 may bias auxiliary swing arm 200 toward master piston 114. In such embodiments, extending master piston 114 from piston bore 112 may cause auxiliary swing arm 200 to rotate backwards. against biasing spring 210 so that it can contact auxiliary cam 320 only when the master piston is hydraulically extended.
    [036] In other embodiments, the swingarms may include an inlet swingarm 100. The inlet swingarm 100 may be adapted to actuate an engine valve, such as an inlet valve 400, by making contact with it directly or through a valve bridge. The auxiliary swingarm 200 may be adapted to selectively actuate at least one inlet valve 400 by contacting the inlet swingarm 100, and acting through the inlet swingarm on the inlet valve. It is envisaged that an inlet cam can transmit primary valve actuating motion to the inlet swingarm to provide a main inlet event, and an auxiliary cam may transmit auxiliary valve actuating motion to the auxiliary swingarm 200 to supply events auxiliary intakes, such as, for example, exhaust gas recirculation and/or brake gas recirculation.
    [037] Operation according to a first method modality of the present invention, using the system to actuate engine valves shown in figures 1-4, will now be explained. Referring to figures 1-4, engine operation causes camshaft 300 to rotate. Rotation of exhaust cam 310 causes exhaust swing arm 100 to pivot around swing shaft 500 and actuate exhaust valves 400 for main exhaust events in response to the interaction between main exhaust lobe 315 on the exhaust cam and exhaust cam roller 102. Also, each lobe in auxiliary cam 320 can cause auxiliary rocker arm 200 to articulate around rocker shaft 500 in the direction of master piston 114.
    [038] During positive power operation of the system, fluid pressure in the control fluid supply passage 520 may be vented or reduced, which in turn can cause fluid pressure in the control fluid passage 160 (see figures 2 and 4) fan or rewind. Referring to Figure 2, as a result, the internal fluid passages in the control valve piston 130 may interrupt registration with the port connecting the control valve bore 124 to the second fluid passage 162 as the control valve 130 translates. into the control valve bore under the influence of the control valve spring 133. Fluid in the second fluid passage 162 may then vent past the rear of the control valve piston 130 and out of the control valve bore 124. As a result, with reference to Figure 2, master piston 114 may collapse into master piston bore 112 under the influence of master piston spring 120.
    [039] Referring to figure 3, the auxiliary swingarm 200 can be biased towards the auxiliary cam 320 by spring 210. As a result of the master piston 114 being biased into hole 112 and the auxiliary swingarm 200 being biased in the In the direction of the auxiliary cam 320, a thrust space may exist between the valve actuating end 206 of the auxiliary rocker arm 200 and the master piston when the auxiliary cam 320 is in the base circle and fluid pressure in the fluid supply passage 520 is ventilated or reduced. Preferably, this thrust space prevents auxiliary swingarm 200 from engaging with master piston 114 when auxiliary swingarm is pivoted by the lobe or lobes on auxiliary cam 320. Thus, during positive power, movement of auxiliary swingarm 200 in response to the auxiliary cam 320 cannot produce any actuation of master piston 114.
    [040] When auxiliary exhaust valve actuation is desired for engine braking, EGR and/or BGR, the fluid pressure in the control fluid supply passage 520 can be increased. A solenoid actuated valve (not shown) can be used to control the application of increased fluid pressure in the control fluid supply passage 520. Increased fluid pressure in the control fluid supply passage 520 is applied through the first passage of fluid 160 in the exhaust swing arm 100 to the control valve piston 130. When the auxiliary valve drive is engine braking, for example, the control valve piston 130 may be displaced within the control valve bore 124 to an "engine brake on" position (shown in Figure 4), where internal fluid passages in control valve piston 130 are aligned with second fluid passage 162. Check valve 140 can prevent fluid which enters the second fluid passage 162 flows back through the control valve piston 130. Fluid pressure in the second fluid passage 162 and the third fluid passage 164 may be sufficient to overcome the biasing force of master piston spring 120. As a result, master piston 114 may extend out of bore 112 and occupy the thrust space between master piston and arm drive end auxiliary swing 206 when auxiliary cam 320 is on the base circle. As long as low pressure fluid holds control valve piston 130 in the “engine brake on” position, master piston 114 can be in a hydraulically extended position. Then, articulation of the auxiliary swingarm 200 by the auxiliary cam 320 can displace the master piston 114, which in turn displaces the slave piston 172 to produce a valve drive for the exhaust valve 400 that is in contact with the piston pin. slip 460. The valve drive can match each lobe on the auxiliary cam (ie, lobes 330, 340, and/or 350) because there is little or no thrust space between the auxiliary swingarm and the master piston.
    [041] When auxiliary exhaust valve actuation is no longer desired, pressure in control fluid supply passage 520 may be reduced or vented and control valve piston 130 will return to an "engine brake off" position. Fluid in master piston bore 112 may then vent back through third and second fluid passages 162 and 164 and out of control valve bore 124.
    [042] It will be apparent to those skilled in the art that variations and modifications of the present invention can be made without departing from the scope or spirit of the invention. For example, it is realized that the exhaust swing arm 100 could be implemented as an intake swing arm, or as an auxiliary swing arm, without departing from the intended scope of the invention. Furthermore, various embodiments of the invention may or may not include a device for biasing the auxiliary swingarm 200 in the direction of the auxiliary cam 320 or the master piston 114. Still further, designating a swingarm as an "auxiliary" swingarm it is not proposed to be limiting its size or shape compared to any other swingarm. These and other modifications to the above-described embodiments of the invention can be made without departing from the intended scope of the invention.
    权利要求:
    Claims (19)
    [0001]
    1. A system for actuating the first and second engine valves (400) associated with the same engine cylinder, comprising: a rocker arm shaft (500); a device for transmitting primary valve actuating motion (310); a primary rocker arm (100) disposed on the rocker arm shaft (500), said primary rocker arm (100) being adapted to drive the first and second motor valves (400) and to receive movement from the device to transmit driving motion. primary valve (310); an auxiliary swing arm (200) disposed adjacent to the primary swing arm (100), a master piston (114) disposed in a master piston hole (112) in the primary swing arm (100) and arranged to receive the drive movements auxiliary swingarm auxiliary valve (200); a slave piston (172) disposed in a slave piston bore (170) in the primary swingarm (100); a control valve (130) disposed in a control valve hole (124) in the primary rocker arm (100); and a hydraulic circuit (162, 164) connecting the master piston hole (112), the slave piston hole (170) and the control valve hole (124), CHARACTERIZED by the fact that a device for transmitting driving movement auxiliary valve (320); said auxiliary swing arm (200) being adapted to receive movement from the device to transmit auxiliary valve actuating movement (320); and said slave piston (172) positioned to provide auxiliary valve actuating movement (320) only to the first of the first and second engine valves (400).
    [0002]
    2. System according to claim 1, CHARACTERIZED by the fact that it additionally comprises: a sliding pin (460) disposed between the slave piston (172) and the first engine valve, in which the auxiliary valve actuation movement (320) is transferred from the auxiliary swingarm (200) to the first engine valve by movement of the master piston (114), slave piston (172) and slide pin (460).
    [0003]
    3. System according to claim 2, CHARACTERIZED in that it further comprises: a valve bridge (450) extending between the first and second engine valves (400), said valve bridge (450) having a side opening extending through a first end of the valve bridge above the first motor valve, wherein said slide pin (460) is disposed in the valve bridge side opening.
    [0004]
    4. System according to claim 1, CHARACTERIZED in that it further comprises: a valve bridge (450) extending between the first and second engine valves (400), said valve bridge (450) having a side opening extending through a first end of the valve bridge above the first engine valve; and a slide pin (460) disposed in the valve bridge side opening and extending between the first engine valve and the slave piston (172).
    [0005]
    5. The system of claim 4, CHARACTERIZED in that it further comprises: a master piston boss (110) extending laterally from a main body of the primary swingarm (100), said master piston boss (110 ) being positioned below a valve drive end (206) of the auxiliary rocker arm (200) and containing the master piston hole (112).
    [0006]
    6. The system according to claim 3, CHARACTERIZED by the fact that it further comprises: a master piston boss (110) extending laterally from a main body of the primary swingarm (100), said master piston boss (110 ) being positioned below a valve drive end (206) of the auxiliary rocker arm (200) and containing the master piston hole (112).
    [0007]
    7. The system according to claim 1, CHARACTERIZED by the fact that it further comprises: a master piston boss (110) extending laterally from a main body of the primary swingarm (100), said master piston boss (110 ) being positioned below a valve drive end (206) of the auxiliary rocker arm (200) and containing the master piston hole (112).
    [0008]
    8. System according to claim 4, CHARACTERIZED by the fact that the master piston (114) extends from an upper surface of the primary swing arm (100) and the slave piston (172) extends from a lower surface of the arm primary oscillating (100).
    [0009]
    9. System according to claim 3, CHARACTERIZED by the fact that the master piston (114) extends from an upper surface of the primary swing arm (100) and the slave piston (172) extends from a lower surface of the arm primary oscillating (100).
    [0010]
    10. System according to claim 1, CHARACTERIZED by the fact that the master piston (114) extends from an upper surface of the primary swing arm (100) and the slave piston (172) extends from a lower surface of the arm primary oscillating (100).
    [0011]
    11. System, according to claim 1, CHARACTERIZED by the fact that it additionally comprises: an engine braking controller; and devices for supplying (160) the master piston bore (112), slave piston bore (170) and hydraulic circuit (162, 164) with hydraulic fluid in response to a signal provided by the engine brake controller.
    [0012]
    12. System according to claim 1, CHARACTERIZED by the fact that it additionally comprises a check valve (140) arranged in the control valve (130).
    [0013]
    13. System according to claim 1, CHARACTERIZED in that it additionally comprises a control fluid supply passage (160) provided in the oscillating shaft and connecting to the hydraulic circuit (162, 164).
    [0014]
    14. System according to claim 1, CHARACTERIZED by the fact that it additionally comprises a master piston spring (120) predisposing the master piston into the master piston hole (112).
    [0015]
    15. System according to claim 1, CHARACTERIZED by the fact that it additionally comprises a slave piston spring (176) predisposing the slave piston (172) into the slave piston bore (170).
    [0016]
    16. System according to claim 1, CHARACTERIZED by the fact that it additionally comprises a device to predispose the auxiliary swing arm (200) towards the master piston (114).
    [0017]
    17. System according to claim 1, CHARACTERIZED by the fact that the auxiliary valve drive movement (320) is selected from the group consisting of: engine braking movement (610, 620), gas recirculation movement of exhaust (640), auxiliary intake movement and brake gas recirculation movement (630).
    [0018]
    18. Method of actuating the first and second engine valves (400) for primary and auxiliary valve actuation events using a primary swing arm (100), an auxiliary swing arm (200) mounted adjacent to the primary swing arm (100), and a master-slave hydraulic lost motion system (114, 172, 162, 164) incorporated into the primary swing arm (100), said method comprising the steps of: actuating the first and second engine valves (400) to a primary valve (310) actuation event responsive to motion transmitted from a first valve train element (310) to the primary rocker arm (100) during a primary valve (310) actuation mode of engine operation; and CHARACTERIZED by the fact that it additionally comprises the steps of: applying hydraulic fluid to the master-slave hydraulic lost motion system (114, 172, 162, 164) to extend master and slave pistons (114, 172) from the swingarm primary (100) during a time in which an auxiliary valve actuation event (320) is to be transmitted only to the first of the first and second engine valves (400); actuate only the first of the first and second engine valves (400) for an auxiliary valve actuation event (320) using the master-slave hydraulic lost motion system (114, 172, 162, 164) responsive to transmitted motion from a second valve train element (310) to the auxiliary rocker arm (200) during an auxiliary valve drive (320) mode of engine operation.
    [0019]
    19. Method according to claim 18, CHARACTERIZED by the fact that the auxiliary valve actuation event (320) is selected from the group consisting of: a compression release motor braking event (610), an event of exhaust gas recirculation (640), an inlet valve event and a brake gas recirculation event (630).
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    同族专利:
    公开号 | 公开日
    CN103597174B|2016-07-27|
    EP2715076A1|2014-04-09|
    JP2014515456A|2014-06-30|
    US8627791B2|2014-01-14|
    US20120298057A1|2012-11-29|
    KR20140036266A|2014-03-25|
    BR112013029941A2|2017-08-08|
    CN103597174A|2014-02-19|
    EP2715076B1|2016-04-20|
    EP2715076A4|2015-03-04|
    KR101569663B1|2015-11-17|
    WO2012162616A1|2012-11-29|
    US20140109848A1|2014-04-24|
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    法律状态:
    2018-12-11| B06F| Objections, documents and/or translations needed after an examination request according [chapter 6.6 patent gazette]|
    2019-12-31| B06U| Preliminary requirement: requests with searches performed by other patent offices: procedure suspended [chapter 6.21 patent gazette]|
    2021-05-04| B09A| Decision: intention to grant [chapter 9.1 patent gazette]|
    2021-06-01| B16A| Patent or certificate of addition of invention granted [chapter 16.1 patent gazette]|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 25/05/2012, OBSERVADAS AS CONDICOES LEGAIS. |
    优先权:
    申请号 | 申请日 | 专利标题
    US201161490544P| true| 2011-05-26|2011-05-26|
    US61/490.544|2011-05-26|
    PCT/US2012/039599|WO2012162616A1|2011-05-26|2012-05-25|Primary and auxiliary rocker arm assembly for engine valve actuation|
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