CN117514404A - Rocker arm assembly including swing arm - Google Patents

Abstract

A rocker arm assembly includes a first rocker arm having a first valve end, a second rocker arm having a second valve end, a first valve, a second valve, a hydraulic capsule disposed in the first valve end and movable between extended and retracted positions, and a rocker arm selectively actuatable by either the first rocker arm or the second rocker arm and spanning the first valve and the second valve. In engine braking mode, the hydraulic capsule is moved to the extended position such that the swing bridge swings angularly as the first rocker arm rotates to actuate the first valve and not the second valve. In a drive mode, the hydraulic capsule moves to the retracted position and the swing bridge is actuated by the second valve end of the second rocker arm when the second rocker arm rotates to actuate both the first valve and the second valve.

Description

Rocker arm assembly including swing arm

Cross Reference to Related Applications

The present disclosure is based on and claims the benefits of U.S. provisional application 63/394,999 entitled "Swing bridge" filed on 8 th month 4 of 2022 and U.S. provisional application 63/387,025 entitled "Swing bridge with hydraulic capsule in dedicated rocker arm for engine brake" filed on 12 th month 12 of 2022, each of which is incorporated herein by reference in its entirety.

Technical Field

The present disclosure relates generally to valve train systems, and more particularly to a rocker arm assembly including a rocker arm.

Background

For the purpose of controlling valve actuation (such as for a main exhaust event), various valve system designs have been produced in the past for use in connection with internal combustion engines. Generally, in a typical valve train, a rocker arm system is coupled to a camshaft via a valve bridge on one side and to a plurality of engine valves via a valve bridge on the other side for synchronously delivering actuation motion from the camshaft to the downstream valves. In some scenarios, it may be desirable to provide auxiliary functions, such as compression engine braking, in addition to the main lift event so that selected valves may be controlled individually. To achieve this, switchable systems are generally employed that are selectively translatable between a retracted position, which inhibits actuation of the associated valve by the corresponding dedicated rocker arm, and an extended position, which allows actuation of the valve. Correspondingly, the valve bridge may also be equipped with a motion transfer mechanism for independently actuating selected valves without affecting other valves. However, current designs typically utilize sliding members that move up and down within the valve bridge, which introduces force balancing problems and occupies a relatively large footprint.

Accordingly, there is a need to provide a solution that not only requires less space, but also provides improved system dynamics.

Disclosure of Invention

The present disclosure proposes a rocker arm assembly having a rocker arm that is capable of rocking as needed to actuate at least one selected valve separate from all valves in order to achieve auxiliary valve function. By employing a rocker mechanism that can transfer motion from a rocker arm to an associated valve while moving relative to a rocker arm, the systems disclosed herein may achieve better force and/or motion transfer, reduce undesirable wear in various valve train components, and improve the dynamic performance of the overall assembly. Further, embodiments according to the present disclosure may provide packaging advantages and lower requirements in terms of space requirements.

In one embodiment, a rocker arm assembly operable in a drive mode and an engine braking mode is provided. The rocker arm assembly includes a first rocker arm having a first valve end, a second rocker arm having a second valve end, a first valve, a second valve, a hydraulic capsule disposed in the first valve end and movable between an extended position and a retracted position, and a rocker arm configured to be selectively actuated by either the first rocker arm or the second rocker arm and span the first valve and the second valve. In particular, in the engine braking mode, the hydraulic capsule is moved to the extended position such that the swing arm swings angularly as the first rocker arm rotates so as to actuate the first valve and not the second valve. And in the drive mode, the hydraulic capsule moves to the retracted position and the swing bridge is actuated by the second valve end of the second rocker arm as the second rocker arm rotates to actuate both the first valve and the second valve.

In particular embodiments, the rocker arm assembly further comprises a first cam for actuating the first rocker arm and a second cam for actuating the second rocker arm.

In particular embodiments, the second rocker arm is deactivated or on the base circle of the second cam in the engine braking mode.

In a particular embodiment, in the drive mode, the first rocker arm is deactivated or on the base circle of the first cam.

In a specific embodiment, the swing arm includes a swing mechanism vertically aligned with the hydraulic capsule.

In particular embodiments, the center of the rocking bridge is vertically aligned with the second valve end.

In particular embodiments, in the drive mode, when the rocking bridge is actuated by the second rocker arm, the horizontal axis of the rocking bridge remains perpendicular to the axis of both the first valve and the second valve.

In particular embodiments, in the engine braking mode, the rocking arm tilts about the tip of the second valve when the rocking arm rocks angularly when actuated by the hydraulic capsule.

In a specific embodiment, the vertical axis of the oscillating mechanism is parallel to the axis of the first valve during the whole operation.

In particular embodiments, the hydraulic capsule includes a plunger configured to be hydraulically controlled to move between an extended position allowing contact with the oscillating bridge and a retracted position avoiding contact with the oscillating bridge.

In one embodiment, a rocker arm assembly includes a first rocker arm having a first valve end, a second rocker arm having a second valve end, a first valve, a second valve, a hydraulic capsule disposed in the first valve end and movable between an extended position and a retracted position, and a rocker arm configured to be selectively actuated by either the first rocker arm or the second rocker arm and span the first valve and the second valve. Specifically, the swing bridge includes a bridge body including a through bore and an orifice intersecting the through bore, and a swing mechanism configured to be connected between the hydraulic capsule and the first valve. The swing mechanism includes a swing pin configured to swing in the through hole, and a rotary cylinder configured to support the swing pin and rotate in the orifice. In addition, the rocker arm is further configured to angularly oscillate when actuated by the hydraulic capsule to actuate the first valve without actuating the second valve, and to actuate both the first valve and the second valve when actuated by the second rocker arm.

In a specific embodiment, in the retracted position of the hydraulic capsule, the hydraulic capsule does not engage the swing mechanism during rotation of the first rocker arm. Further, in the extended position of the hydraulic capsule, at least a portion of the hydraulic capsule extends outwardly from the first valve end and is capable of engaging the swing mechanism during rotation of the first rocker arm.

In a specific embodiment, the swing mechanism further comprises a first contact area for contacting the hydraulic capsule, and the bridge body comprises a second contact area for contacting the second valve end.

In a specific embodiment, the swing mechanism is located on one side of the swing arm and vertically aligned with the hydraulic capsule.

In particular embodiments, the second contact region is located near the center of the swing bridge and vertically aligned with the second valve end.

In a specific embodiment, the through holes are arranged in a vertical direction.

In a specific embodiment, the aperture is arranged perpendicular to the through hole.

In a specific embodiment, the rotary cylinder is axially fixed by the oscillating pin.

In a specific embodiment, the long axis of the rotary cylinder is perpendicular to the long axis of the swing pin.

In a specific embodiment, a gap is defined between the swing pin and the through hole so as to allow the swing pin to swing inside the through hole.

Drawings

Embodiments according to the present disclosure will now be described with reference to the accompanying drawings, in which:

FIG. 1 illustrates a rocker arm assembly including a swing arm according to the present disclosure;

FIG. 2 illustrates a partial cross-sectional view of the rocker arm assembly of FIG. 1;

FIG. 3 illustrates a cross-sectional view of a hydraulic capsule according to the present disclosure;

FIG. 4 shows an independent view of the swing arm of FIG. 1;

fig. 5 to 6 show two exploded views of the oscillating arm taken from different angles;

fig. 7 shows a schematic cross section of a swinging cross arm;

FIG. 8 shows the swing arm in a drive mode;

fig. 9 shows the swing arm in auxiliary mode;

fig. 10 illustrates another embodiment of a swing arm according to the present disclosure;

FIG. 11 shows an exploded view of the swing arm of FIG. 10;

FIG. 12 shows a cross-sectional view of the swing arm of FIG. 10;

fig. 13 illustrates yet another embodiment of a swing arm according to the present disclosure;

FIG. 14 shows an exploded view of the swing arm of FIG. 13; and is also provided with

Fig. 15 shows a cross-sectional view of the swing arm of fig. 13.

Detailed Description

Reference will now be made in detail to examples shown in the accompanying drawings. Wherever possible, the same reference numbers will be used throughout the drawings to refer to the same or like parts. Directional references such as "upper", "lower", "right" and "left" are for ease of reference to the drawings and are not intended to limit the scope of the present disclosure.

Fig. 1-2 illustrate an exemplary rocker arm assembly 100 having a swing arm 102 according to one embodiment of the present disclosure. In the illustrated embodiment, the rocker arm assembly 100 may generally include a primary rocker arm 104, such as a primary exhaust rocker arm, and an auxiliary or auxiliary rocker arm 106, such as an engine brake rocker arm. The primary rocker arm 104 and the auxiliary rocker arm 106 may cooperate (e.g., under a control strategy or method) to selectively actuate the first and second engine valves 108, 110 via a rocker arm 102 connected between the rocker arms 104, 106 and the engine valves 108, 110. More specifically, for example, the first engine valve 108 may be actuated separately from the second engine valve 110 such that the first engine valve 108 may operate on a lift profile associated with the auxiliary rocker arm 106 and the second engine valve 110 may operate on another lift profile associated with the primary rocker arm 104, the details of which will be appreciated from the discussion below.

While specific embodiments of the present disclosure may be set forth in the context of rocker arms for operating exhaust valves in an engine braking system, such as in 1.5 or 2-stroke compression braking, for example, those skilled in the art will appreciate that the present disclosure is not limited to such applications. Various embodiments according to the present disclosure may be equally or similarly applicable to other types of systems in valve train assemblies. For example, embodiments of the present disclosure may be used in conjunction with an intake rocker arm system, an extended valve closing system, an early valve opening system, or other suitable valve train system familiar to those skilled in the art.

With continued reference to fig. 1-2, in particular embodiments, the primary rocker arm 104 may be pivotably supported by a rocker shaft (not shown) extending through the central opening 112 such that the primary rocker arm 104 may rotate about the rocker shaft based on the cam lift profile of the primary lift cam 114. Specifically, the cam end 116 of the primary rocker arm 104 may contact or otherwise be coupled to the main lift cam 114 for receiving valve actuation motion. The valve end 118, opposite the cam end 116, may in turn be configured to engage the rocker arm 102 as the primary rocker arm 104 rotates to transfer motion from the main lift cam 114 to both engine valves 108 and 110 coupled to the rocker arm 102. Similarly, in particular embodiments, an auxiliary rocker arm 106, which may be disposed parallel to the primary rocker arm 104, for example, may also be rotatably supported by a camshaft. As shown, the auxiliary rocker arm 106 may include a cam end 122 for receiving valve actuation motion from an auxiliary lift cam 120 (e.g., an engine brake lift cam) and a valve end 124 opposite the cam end 122 and configured to selectively engage a rocker mechanism 126 of the rocker arm 102 as desired. In particular embodiments, the rocker mechanism 126 may be configured to transfer actuation motion from the auxiliary rocker arm 106 to one engine valve, such as the first engine valve 108 associated with engine braking, while allowing the rocker arm 102 to rock an angle in a manner that avoids actuation of another engine valve, such as the second engine valve 110. Details of the swing mechanism 126 and the swing arm 102 will be described more fully below with reference to fig. 4-6.

In particular embodiments, it may be desirable to configure the auxiliary rocker arm 106 to be selectively switchable so that it can be selected whether the auxiliary lift cam 120 can actuate the associated engine valve 108. That is, the auxiliary rocker arm 106 may transition between a primary mode (i.e., the valve end 124 is spaced from contact with respect to the rocker arm 102, and thus the associated engine valve 108 remains unactuated regardless of the rotation of the auxiliary rocker arm 106) and an auxiliary mode (i.e., the valve end 124 engages the rocker arm 102 via the rocker mechanism 126 as the auxiliary rocker arm 106 reciprocates, allowing motion to be delivered to the engine valve 108). To this end, a hydraulic capsule 128 may be provided at the valve end 124 of the auxiliary rocker arm 106. The hydraulic capsule 128 may be hydraulically controlled by pressurized fluid supplied via a fluid circuit passing through the auxiliary rocker arm 106 and configured to move between a retracted position and an extended position. In particular embodiments, for example, hydraulic capsule 128 may be received by a vertical aperture disposed in valve end 124 of auxiliary rocker arm 106. During operation, hydraulic capsule 128 may be actuated to protrude outwardly from the bottom of valve end 124 to contact swing mechanism 126 or retract into valve end 124 to avoid contact with swing mechanism 126, as desired.

Fig. 3 shows an isolated cross-sectional view of the hydraulic capsule 128 in more detail, in particular showing the hydraulic capsule 128 in its retracted state. In particular embodiments, hydraulic capsule 128 may include a housing 304 that is generally cylindrical in shape and may include an upper chamber 306 and a lower chamber 308. In the example shown, the upper chamber 306 and the lower chamber 308 may together form a single body defining the housing 304 for containing and/or containing the various components of the hydraulic capsule 128 in a serial fashion. For example, the upper chamber 306 may house a pin 310, while the lower chamber 308 may house a check valve assembly 312 and a plunger 314, each aligned along the pod axis 302.

As shown in FIG. 3, the upper chamber 306 may be provided with one or more fluid passages 316, which may be, for example, circumferentially disposed on a sidewall of the upper chamber 306 and configured to receive hydraulic fluid (e.g., oil) supplied via the auxiliary rocker arm 106. The lower chamber 308 may be positioned below the upper chamber 306 and configured to be in fluid communication with the upper chamber 306 via an opening 318 disposed between the upper chamber 306 and the lower chamber 308. In this manner, pressurized fluid introduced into the upper chamber 306 through the fluid passage 316 may be allowed to enter the lower chamber 308 via the opening 318—for example, in a selective manner under the control of the check valve assembly 312, the details of which will be explained more clearly below.

As further shown in fig. 3, the upper chamber 306 may contain a pin 310. The pin 310 may be hydraulically controlled by the pressure of fluid introduced into the upper chamber 306 to compress and/or extend vertically along the pod shaft 302. For example, in the depicted configuration, the spring 320 may be coupled to a top end of the pin 310 and configured to bias the pin 310 downward to its extended position. When fluid flows in and hydraulic pressure builds up inside the upper chamber 306, the hydraulic pressure may overcome the downward biasing force exerted by the spring 320, thus pushing the pin 310 in an upward direction into a retracted state. In particular embodiments, the check valve assembly 312 downstream of the pin 310 may be configured to selectively enable fluid communication between the upper chamber 306 and the lower chamber 308 based on movement of the pin 310. The check valve assembly 312 may be disposed in the lower chamber 308 at a location directly below the opening 318. In the embodiment shown, the check valve assembly 312 includes a check ball 322 that may be depressed by the pin 310 to open a fluid passage through the opening 318. During operation, the check ball 322 may generally seat against the opening 318, such as by pushing the check ball 322 upward with the valve spring 324. In this way, when biased, the check ball 322 may become a one-way valve that allows fluid to flow down to the lower chamber 308, but prevents it from flowing back in the opposite direction to the upper chamber 306. When the pin 310 is moved to its extended position, the lower terminal end of the pin 310 may protrude into the opening 318 and push against the check ball 322, thereby unseating the check ball 322 from the opening 318 and allowing fluid to flow through the check ball 322 into the lower chamber 308, or vice versa.

With continued reference to fig. 3, the lower chamber 308 may further house a plunger 314. For example, the plunger 314 may be disposed below and in line with the check valve assembly 312. In particular embodiments, plunger 314 is configured to translate a distance (e.g., vertically along capsule axis 302) inside lower chamber 308 between an extended position and a retracted position upon actuation of fluid introduced into lower chamber 308. For example, when the lower chamber 308 is filled with pressurized fluid, the plunger 314 may be hydraulically actuated in a downward direction to a position in which the lower end of the plunger 314 extends from the bottom of the hydraulic capsule 128. In this case, as the auxiliary rocker arm 106 rotates, the plunger 314 may contact the rocker arm 102, thereby enabling movement to be transferred to the downstream engine valve 108. In particular embodiments, the spring 326 may be coupled to the plunger 314, for example, near a lower end of the plunger 314. For example, a spring seat 328 may be provided to support the spring 326 upward, which is attached or secured into the end of the lower chamber 308. As indicated by the arrow in fig. 3, the spring 326 may provide an upward spring force to the plunger 314 such that when fluid pressure is removed, the plunger 314 may return to the retracted state. In this retracted configuration, most or all of the plunger 314 may be substantially contained within the lower chamber 308 in a manner that inhibits contact with the rocker arm 102 even when the auxiliary rocker arm 106 rotates, thus disabling the engine valve 108 as desired. In other words, by configuring the hydraulic capsule 128 in this manner, a variable volume may be created that expands when pressurized fluid reaches the lower chamber 308 through the check valve assembly 312 and pushes the plunger 314 downward, and contracts when the check valve assembly 312 is opened to release fluid from the lower chamber 308, thereby switching the hydraulic capsule 128 between the extended and retracted states.

The design of the hydraulic capsule 128 disclosed herein contrasts with prior art designs in that the plunger 314 may be held in default compression by the spring 326 when deactivation is required, thereby avoiding any contact between the hydraulic capsule 128 and the swing arm 102. This may protect the system from undesirable wear, reduce the risk of damaging the movable components, and help maintain proper system dynamics.

While depicted and described in this particular manner, those skilled in the art will appreciate that the rocker arm assembly disclosed herein is provided for illustrative purposes only and is not intended to limit the scope of the present disclosure. Other suitable configurations are also contemplated by the present disclosure. For example, certain embodiments according to the present disclosure may include only some, if not all, of the structures described above without departing from the scope of the present disclosure. Alternatively, other additional features may be optionally provided as are familiar in the art and will not be described in detail herein.

Fig. 4 shows an isometric view of the swing arm 102 with the swing mechanism 126 according to the present disclosure, and fig. 5-6 show various exploded views of the swing arm 102 taken from different angles. In particular embodiments, the swing bridge 102 may be configured to span and lie atop the engine valves 108 and 110. For example, and not by way of limitation, in the depicted embodiment, the body 400 of the swing bridge 102 may include a first valve side 402 operatively coupled to a terminal end of the engine valve 110, and a second valve side 404 generally opposite the engine valve side 402 and operatively coupled to a terminal end of the engine valve 108. For example, in some embodiments, the second valve side 404 may be provided with a valve seat 602 at its bottom that may rest on and receive the top of the engine valve 110. Although depicted as a circular depression, the valve seat 602 may take the form of a different shape, such as an oval, elongated, circular, or other suitable shape familiar to those skilled in the art. Further, the top surface of the body 400 may be provided with a contact area 406, which may be located near the center of the body 400 in a position vertically aligned with the valve end 118 of the primary rocker arm 104. During operation, as the primary rocker arm 104 is depressed, the contact region 406 may engage the valve end 118 to transfer motion downstream (i.e., in the direction of force transfer) to actuate both engine valves 108 and 110. For example, the contact area 406 may be substantially flat to better maintain contact and ensure proper motion and/or force delivery. Of course, other suitable surface structures, such as curved or concave surface areas, are also contemplated by the present disclosure for performing the desired motion transfer function.

With continued reference to fig. 4-6, in particular embodiments, the swing mechanism 126 may be disposed at the first valve side 402 to engage or contact the engine valve 108, for example, associated with engine braking. The swing mechanism 126 may generally include a swing pin 502 and a rotary cylinder 504 supporting the swing pin 502 (e.g., vertically upward as shown). For example and without limitation, in the embodiment shown, the long axis 510 of the swing pin 502 may be disposed perpendicular to the long axis 512 of the rotary cylinder 504. To accommodate the swing pin 502 and the rotary cylinder 504, respectively, the first valve side 402 may be correspondingly configured with a through hole 506 that may extend in a vertical direction inside the body 400, for example, and an aperture 508 that may intersect the through hole 506 horizontally. Specifically, in particular embodiments, the length of the rotary cylinder 504 (e.g., measured along the long axis 512) may be substantially equal to the length of the aperture 508 such that, when inserted, the rotary cylinder 504 may engage at least a portion of the body 400. So configured, during assembly of the illustrated embodiment, the rotary cylinder 504 may first be fitted into the aperture 508 such that its long axis 512 is aligned with the central axis of the aperture 508. Thereafter, the swing pin 502 may be inserted into the through hole 506 so as to abut against and engage the rotary cylinder 504.

As further shown, in this example embodiment, the swing pin 502 may be generally cylindrical in structure. However, other suitable configurations (such as elongated, etc.) are also contemplated for performing the desired functions of the present disclosure. In particular embodiments, the swing pin 502 may include a contact surface at an upper end thereof for contacting the hydraulic capsule 128 to receive actuation motions therefrom. Further, the swing pin 502 may also include an insert 514 (e.g., in the form of a protrusion) extending from a lower end thereof for engagement with the rotary cylinder 504. Accordingly, the upper surface of the rotary cylinder 504 may be provided with a recess or slot 516 shaped to mate with the insert 514 and/or the lower end of the swing pin 502 such that the insert 514 and/or the lower end may fit tightly into the slot 516 to axially secure the rotary cylinder 504. In addition or alternatively, other suitable connection or mating structures or methods (such as a snap fit, interference fit, etc.) may be employed to properly secure the swing pin 502 and the rotary cylinder 504 together. Configured in this manner, the rotary cylinder 504 is able to maintain firm engagement with the swing pin 502 while providing support for the swing pin 502.

In the embodiment shown, the lower surface of the rotary cylinder 504 may be configured with a valve seat 604 that may remain in contact with the terminal end of the engine valve 108 during overall system operation. For example, and not by way of limitation, the valve seat 604 may include a substantially flat region that rests on top of the valve tip to ensure proper contact with the engine valve 108 to transfer actuation movement to the engine valve 108 as desired. Alternatively or in addition, although not shown, optional retention features such as clamps or the like may be provided at the valve seat 604 to provide additional degrees of securement. Of course, other suitable surface structures familiar to those skilled in the art, such as curved surface areas, are also contemplated by the present disclosure for performing the intended function of engaging an engine valve.

Fig. 7 schematically depicts a cross section of the oscillating arm 102 taken along the longitudinal axis. As can be clearly seen in this illustration, a gap 700 may be defined between the swing pin 502 and the through hole 506, such as specifically between an outer wall of the swing pin 502 and an inner side of the through hole 506. In other words, the through-hole 506 may be sized such that the width 702 is relatively larger than the outer diameter or width 704 of the swing pin 502. In this manner, spatial redundancy may be allowed to include the swing pin 502 in a manner that accommodates the swing of the swing pin 502 inside the through hole 506.

The operation of the swing arm 102 according to the present disclosure will be explained with reference to fig. 8-9, wherein fig. 8 shows the swing arm 102 in a drive mode, i.e., during a main lift event of the primary rocker arm 104, and fig. 9 shows the swing arm 102 in an auxiliary mode, such as in an engine braking mode, wherein the auxiliary rocker arm 106 is activated to selectively engage the swing arm 102 as desired.

Referring to FIG. 8, wherein the left side cross-sectional view is taken from the front of the valve bridge 102 and the right side cross-sectional view is taken from the first valve side 402 of the valve bridge 102, in a drive mode, the primary rocker arm 104 may rock (e.g., in response to a main lift profile) and act on the rocker bridge 102 by pressing a contact area 406 located at the middle of the rocker bridge 102, pushing the rocker bridge 102 vertically downward (as indicated by the arrow in the figure) to drive open both engine valves 108 and 110 simultaneously. For example, the engine valves 108 and 110 may be moved to the same valve position in synchronization with each other. Further, during this process, the horizontal axis of the swing bridge 102 may remain substantially perpendicular to the axis of both engine valves 108 and 110.

Additionally, the auxiliary rocker arm 106 may be located on the base circle or deactivated when in the drive mode. Alternatively or in addition, the hydraulic capsule 128 may retract to inhibit contact with the swing arm 102 even when the auxiliary rocker 106 rotates such that the swing arm 102 (specifically, the swing mechanism 126) receives zero actuation motion from the auxiliary rocker 106.

Referring to FIG. 9, wherein the left side cross-sectional view is taken from the front of the valve bridge 102 and the right side cross-sectional view is taken from the first valve side 402 of the valve bridge 102, in the auxiliary mode, the primary rocker arm 104 may be located on a base circle or deactivated and the auxiliary rocker arm 106 may rotate according to the lift profile of the auxiliary lift cam 120. In addition, hydraulic capsule 128 is controllably extended such that plunger 314 may act through swing mechanism 126 (as indicated by the arrow in the figure) to move engine valve 110 independently of engine valve 108. That is, the engine valve 110 remains unactuated regardless of the movement of the second rocker arm 104. During this auxiliary valve lift event, the long axis 510 of the rocker pin 502 may remain parallel to or in line with the axis of the engine valve 108 by virtue of the relative rotation of the rotary cylinder 504 within the orifice 508. At the same time, the rocking bridge 102 may tilt-e.g., pivot slightly downward about the second valve side 404-although the rocking pin 502 and the valve axis of the engine valve 108 are in parallel positions. As already explained, a gap 700 may be provided to allow the swing cross arm 102 to move relative to the swing pin 502. Optionally, in particular embodiments, the valve seat 602 may be further sized deep enough to accommodate such rocking or tilting of the rocking bridge 102 to ensure proper contact with the engine valve 110 throughout operation.

Fig. 10-12 illustrate another configuration of a rocking bridge 1002 according to the present disclosure, which is similar in result to the rocking bridge 102 described above, in that it includes a body 1004 having a first valve side 1006 associated with an engine valve 110, a second valve side 1008 opposite the first valve side 1006 and associated with the engine valve 108, and a rocking mechanism 1010 located at the first valve side 1006. In particular embodiments, swing mechanism 1010 may have a swing pin 1102 and a rotating cylinder 1104 that supports swing pin 1102 (e.g., vertically upward as shown in the figures). For example and without limitation, in the embodiment shown, the long axis 1106 of the swing pin 1102 may be disposed perpendicular to the long axis 1108 of the rotary cylinder 1104. To accommodate the swing pin 1102 and the rotary cylinder 1104, respectively, the first valve side 1006 may be correspondingly configured with a through-hole 1110 that may extend in a vertical direction inside the main body 1004, for example, and an aperture 1112 that may intersect the through-hole 1110 horizontally.

In this embodiment as shown, the swing pin 1102 may be elongated and include a through bore 1114 extending perpendicular to the long axis 1106 and configured to rotatably receive the rotary cylinder 1104. In this configuration, during assembly, the swing pin 1102 may first be inserted into the through hole 1110 to a position in which the through hole 1114 is aligned with the aperture 1112. Thereafter, the rotary cylinder 1104 may be fitted into the aperture 1112 and passed through the through-hole 1114 to support the swing pin 1102 relative to the main body 1004.

Additionally, as further shown, the swing pin 1102 may also include a contact surface 1116 at an upper end thereof for contacting the hydraulic capsule 128 for receiving actuation motions. For example, and without limitation, the contact surface 1116 may be formed as a platform extending upwardly from the upper end of the swing pin 1102. Alternatively, other possible surface structures may be provided for transferring motion as desired. In the embodiment shown, the swing pin 1102 additionally includes a valve seat 1202 disposed at a lower end thereof. For example, the valve seat 1202 may be a circular recess or other suitable structure for engaging the terminal end of the engine valve 108 in a motion transmitting manner. Similarly, the second valve side 1008 may include a valve seat 1204 configured as an elongated pocket or cutout to rest on top of the terminal end of the engine valve 110 and remain in contact throughout operation. Although described in this manner, it should be appreciated that valve seats 1202 and/or 1204 may be differently configured for coupling to engine valves.

Fig. 13-15 illustrate yet another configuration of a swing arm 1302 according to the present disclosure. The rocking bridge 1302 is substantially similar to the rocking bridge 102 except that it further includes an optional valve cover 1402. In particular embodiments, the valve cover 1402 may be removably received by a valve seat 1404 disposed at a lower surface of the rotary cylinder 1406 and configured to cover around a terminal end of the engine valve 108. In such a configuration, for example, the valve seat 1404 may be sized to have a greater depth so as to at least partially contain the valve cover 1402. In this way, proper coupling with the engine valve 108 may be ensured while avoiding unintended disengagement. Furthermore, the rocking bridge 1302 may accommodate various valve sizes without requiring any significant modification.

Various embodiments of the present disclosure may advantageously provide better packaging and lower space requirements due to their implementation of more compact structures. Further, embodiments disclosed herein facilitate better control of motion and/or force transfer and overall system dynamics. It will also be understood that one or more other advantages may be readily apparent to those skilled in the art in view of the drawings, description, and claims of the present disclosure.

In this document, "or" is inclusive rather than exclusive, unless explicitly indicated otherwise or indicated by context. Thus, herein, "a or B" means "A, B or both" unless explicitly indicated otherwise or otherwise by context. Furthermore, "and" are both conjunctive and singular, unless explicitly stated otherwise or indicated by context. Thus, herein, "a and B" means "a and B, either jointly or individually," unless indicated otherwise explicitly or otherwise by context.

The scope of the present disclosure encompasses all changes, substitutions, variations, alterations, and modifications to the example embodiments described or illustrated herein that will be understood by those skilled in the art. The scope of the present disclosure is not limited to the example embodiments described or illustrated herein. Furthermore, although the disclosure describes and illustrates respective embodiments herein as including particular components, elements, features, functions, operations, or steps, any of these embodiments may include any combination or permutation of any of the components, elements, features, functions, operations, or steps described or illustrated anywhere herein that one of ordinary skill in the art would understand. Furthermore, references in the appended claims to an apparatus or system or component of an apparatus or system that is adapted, arranged, capable, constructed, enabled, operable, or operative to perform a particular function include the apparatus, system, component whether or not it or that particular function is activated, turned on, or unlocked, provided that the apparatus, system, or component is so adapted, arranged, capable, constructed, enabled, operable, or operative. Additionally, although the present disclosure describes or illustrates particular embodiments as providing particular advantages, particular embodiments may not provide these advantages, provide some or all of these advantages.

Claims (10)

1. A rocker arm assembly operable in a drive mode and an engine braking mode, the rocker arm assembly comprising:

a first rocker arm having a first valve end;

a second rocker arm having a second valve end;

a first valve;

a second valve;

a hydraulic capsule disposed in the first valve end and movable between an extended position and a retracted position; and

a rocking bridge configured to be selectively actuated by either the first rocker arm or the second rocker arm and to span the first valve and the second valve,

wherein in the engine braking mode, the hydraulic capsule is moved to the extended position such that the swing bridge swings angularly as the first rocker arm rotates to actuate the first valve without actuating the second valve, and

wherein in the drive mode, the hydraulic capsule is moved to the retracted position and the swing bridge is actuated by the second valve end of the second rocker arm when the second rocker arm rotates so as to actuate both the first valve and the second valve.

2. The rocker arm assembly of claim 1, further comprising a first cam for actuating the first rocker arm and a second cam for actuating the second rocker arm.

3. The rocker arm assembly of claim 2 wherein in the engine braking mode, the second rocker arm is deactivated or on the base circle of the second cam.

4. The rocker arm assembly of claim 2 wherein in the drive mode, the first rocker arm is deactivated or on the base circle of the first cam.

5. The rocker arm assembly of claim 1 wherein the swing cross arm includes a swing mechanism vertically aligned with the hydraulic capsule.

6. The rocker arm assembly of claim 1 wherein the center of the rocker arm is vertically aligned with the second valve end.

7. The rocker arm assembly of claim 1 wherein in the drive mode, a horizontal axis of the rocker arm remains perpendicular to axes of the first and second valves when the rocker arm is actuated by the second rocker arm.

8. The rocker arm assembly of claim 1 wherein in the engine braking mode, the rocker arm tilts about the tip of the second valve when the rocker arm is angularly rocked when actuated by the hydraulic capsule.

9. The rocker arm assembly of claim 5 wherein the vertical axis of the rocker mechanism is parallel to the axis of the first valve throughout operation.

10. A rocker arm assembly, comprising:

a first rocker arm having a first valve end;

a second rocker arm having a second valve end;

a first valve;

a second valve;

a hydraulic capsule disposed in the first valve end and movable between an extended position and a retracted position; and

a rocking bridge configured to be selectively actuated by either the first rocker arm or the second rocker arm and to span the first valve and the second valve, the rocking bridge comprising

A cross arm body including a through hole and an orifice intersecting the through hole, and

a swing mechanism configured to be connected between the hydraulic capsule and the first valve, the swing mechanism including

A swing pin configured to swing in the through hole, an

A rotary cylinder configured to support the swing pin and rotate in the aperture;

wherein the swing arm is further configured to:

angularly oscillate when actuated by the hydraulic capsule so as to actuate the first valve and not actuate the second valve; and

both the first valve and the second valve are actuated when actuated by the second rocker arm.