JP2022531009A - Finger follower for lobe switchable and single source lost motion - Google Patents

Abstract

A switchable finger may operate in two or three states or positions and cooperate with a single source of motion to achieve a method of operating the engine in corresponding two or three modes. Modes may include cylinder deactivation, main event mode, or auxiliary modes including lost motion braking, LIVC, and EEVO. A follower for an engine valve mechanism utilizes an adjustable support assembly that eliminates the possibility of partial engagement during operation. A lever engaging member or latch is arranged for movement on the follower body to interact with the lever to provide a constant contact geometry. The latch may support the lever in one or more precise positions, or may allow the lever to pivot freely from the latch to allow full lost motion, such as in cylinder deactivation applications.

Description

Cross-reference to related applications This application is a partial continuation of pending US application No. 16/706,226, filed December 6, 2019, entitled FINGER FOLLOWER FOR LOBE SWITCHING AND SINGLE SOURCE LAST MOTION. And claim its priority. This application claims the priority of US Provisional Patent Application No. 62/776,450, filed December 6, 2018, entitled SWITCHING FINGER FOLLOWER. This application is further filed on December 6, 2018, US Provisional Application No. 62/776,453, entitled SWITCHING FINGER FOLLOWER FOR SINGLE-SOURCE LOST MOTION, and May 28, 2019. Also, the US provisional application No. 62 / 853,599, which is the US provisional application named SWITCHING FINGER FOOLLOWER FOR SINGLE-SOURCE LOST MOTION INCLUDING A THREE-POSITION SWITCHING FINGER FOLLOWER, is claimed. The subject matter of both provisional applications is incorporated herein by reference in their entirety.

The present disclosure relates generally to systems and methods for activating one or more engine valves within an internal combustion engine. More specifically, the present disclosure relates to systems and methods for altering the operational relationship between a source of motion, such as a cam, and one or more engine valves. Such systems and methods may include a rocker arm in the form of a finger follower that provides selective switching between lobes on the cam and / or operation as a lost motion device in the engine valve mechanism. Further, the present disclosure uses valve mechanism components such as finger followers capable of switching between two or three operating states, and such valve mechanism components, such as cylinder deactivation, positive power of the main event, or. It relates to a method of operating an internal combustion engine in different operating modes such as lost motion braking, early exhaust valve opening (EEVO), or auxiliary events such as late intake valve closing (LIVC).

Internal combustion engines are ubiquitously used in many applications and industries, including transportation and trucking. Valve actuation systems used in internal combustion engines are well known in the art. Such a system typically comprises one or more intervening components that transmit the valve actuating motion from the valve actuating motion source (eg, cam) to the one or more engine valves, the intervening component being the valve. It constitutes a mechanism. These valve actuation systems may facilitate a positive power operating mode in which the engine cylinder is primarily powered by the combustion process. The actuation motion of the intake and exhaust valves associated with a standard combustion cycle is typically referred to as the "main event" motion. Known engine valve actuation systems may provide modified main event valve motion, such as early or late intake valve closure. In addition to the main event motion, known engine valve actuation systems allow the internal combustion engine to operate in other modes, or in various positive power generation modes, as an auxiliary valve actuation motion or event (eg, exhaust). Gas recirculation (EGR), early exhaust valve opening (EEVO), etc.), or the deceleration force that helps the internal combustion engine operate as a fuel-free state, essentially as an air compressor, to decelerate the vehicle. The resulting engine brake can be facilitated.

In many engine systems, the valve mechanism may include a finger follower, which is essentially a lever that pivots with one end of the lever in contact with the load, i.e. the engine valve. The finger follower typically contains a motion receiving component disposed between the ends of the lever, which receives a valve actuating motion from a source of motion (such as a cam), which motion then loads the lever. It is transmitted to the engine valve through the end.

Known variants of the above finger follower components include so-called "switchable" finger followers, examples of which are described in US Pat. No. 7,546,822, the subject of which is by reference. Incorporated herein. As shown in FIG. 1, the finger follower, in this example, comprises a body 11 pivoted around a hydraulic rush adjuster (HLA) 2. The body 11 also supports a lateral follower 30 that, in this example, can rotate around the shaft 17 and can engage the locking mechanism 40. As best shown in FIGS. 2 and 3, the body 11 further supports a central roller follower 20 positioned between the side followers 30. As further shown in FIGS. 2 and 3, the locking mechanism 40 maintains the locking bar 48 in the extended position, thereby contacting the tab 38 of the lateral follower 30 (FIG. 2). Or it may be maintained in a retracted position, thereby being controlled to avoid contact with the tab 38 (FIG. 3). When the locking bar 48 contacts the tab 38 (ie, when locked or in the on state), the lateral follower 30 is prevented from rotating around the shaft 17, and thus the body 11 And maintain a solid relationship. Therefore, the motion applied to the lateral follower 30 by the lateral cam lobe 9 is transmitted to the main body and finally to the engine valve 3. In this case, the valve actuation motion provided by the central cam lobe 8 is not transmitted to the central roller follower 20 to which it is aligned. On the other hand, when the locking bar 48 is retracted (ie, in the unlocked or off state), the lateral follower 30 has all the movement applied by the lateral cam lobe 9 absorbed by the lateral follower 30 and the body. It rotates freely around the shaft 17 so as not to be transmitted to the engine valve 3 by 11. In this case, the valve actuating motion provided by the central cam lobe 8 is transmitted to the central roller follower 20 and thereby to the engine valve 3.

Finger follower switching is most common in lightweight automotive applications. However, due to heavy load events and failures due to partially engaged switchable mechanisms, these have not been applied to heavy and medium weight diesel or natural gas engines. It is known that even in lightweight applications, failures occur due to similar partial engagement problems at much lower loads. Referring to the examples of FIGS. 2 and 3, such partial engagement occurs when the locking bar 48 only partially overlaps the tab 38, ie, the position between the engagements shown in FIGS. 2 and 3. Occurs in. When such partial engagement occurs, the contractile stress between the moving parts of the locking mechanism is significantly increased, which can lead to damage and / or failure of the locking mechanism.

Another disadvantage of prior art switchable finger followers is that they are usually controlled for precise timing to prevent partial engagement of their actuation or locking components. It is necessary. This may require additional cost and complexity, especially in a multi-cylinder engine environment. For example, in such an environment, each to eliminate the possibility of control circuit transients (ie, delays in the hydraulic circuit) and to ensure the exact timing of actuating the components to the finger follower motion. It may be necessary to provide a designated control solenoid for the switchable finger follower.

Finger follower switching can be applied to the lost motion valve actuation system. In such a system, the switchable finger follower has a first position where complete valve motion from a source of motion, such as a cam, is transmitted to the engine valve, and only part of the complete valve motion is transmitted to the engine valve. Can switch between and a second position. An example of a single source lost motion lift profile described herein can be found in curve 502 of FIG. 5 of US Pat. No. 9,347,383, the teaching of which is hereby referred to herein. Be incorporated. However, due to the disadvantages mentioned above, the prior art switchable finger followers may have limited applicability to lost motion valve actuation systems.

Therefore, it is advantageous to provide a system and method for dealing with the above-mentioned drawbacks in the prior art.

In response to the aforementioned challenges in the prior art, the present disclosure provides various embodiments of a switchable finger follower system with improved operating characteristics, as well as improved performance and durability.

The above difficulties with conventional switching finger followers can be overcome on the basis of various embodiments disclosed herein. The advances in the art described herein are particularly advantageous in eliminating the possibility of partial engagement of the finger follower switchable mechanism actuating components. A related advantage is that it eliminates variations in the locking or supporting position of the motion receiving component on the switchable finger follower. The switchable finger follower configuration is between the collaborative component, the position of the positively defined switchable mechanism, and thus the position of the positively defined finger follower lever, and thus the motion receiving component with respect to the body. Has a consistent contact shape. This leads to more accurate and reliable valve motion operation and control.

Moreover, the switchable finger follower configurations disclosed herein are not sensitive to partial engagement of the switchable mechanism, activation of the switchable mechanism, so that they are at lower cost and complexity in a multi-cylinder engine environment. It can be used. Therefore, improved switchable mechanisms and actuators eliminate the need for precise timing by control components. For example, in the case of a hydraulically actuated switching mechanism under the control of a solenoid, the disclosed embodiments can eliminate the need for a controlled solenoid designated for each switching mechanism. Rather, the disclosed advances make it feasible for a single solenoid to activate a multi-cylinder switchable mechanism, thereby simplifying the entire system and reducing costs.

Further, in the embodiments described herein, a single valve actuation source (such as a cam) has one or more low lift events in which some (or all) lift is lost, and a cam lobe. Many (or all) lifts from are applicable to a single source lost motion system that provides one or more high lift events transmitted to the engine valve and can be used to improve it. Further, the embodiments described herein are applicable to lost motion valve actuation systems that completely lose valve motion and are used to improve them, as may be required in systems utilizing cylinder deactivation. can do.

The embodiments described herein may be particularly advantageous for achieving alternative valve movements such as late brake intake valve closure (LIVC), early exhaust valve opening (EEVO), internal exhaust gas recirculation (IEGR). ..

According to one aspect of the present disclosure, a follower body having a pivot end and a motion transmission end, a lever adapted to pivot with respect to the follower body, and a pivot end and a follower body of the follower body. An adjustable support assembly that includes a motion receiving component with a motion receiving surface disposed between the motion transmitting ends of the lever and a movable latch to provide selective support to the lever, on the follower body. In contrast, a finger follower system is provided for use in an internal combustion engine valve mechanism comprising an adjustable support assembly adapted to maintain the latch in the first and second latch positions. According to a further aspect, the adjustable support assembly is further adapted to allow the latch to move to the first position when the latch is not in the second position. In some applications, the adjustable support assembly may be further adapted to support the lever in two defined positions, when the latch is in the first latch position, and the latch is in the second latch position. Provides engagement between the lever and the latch when at. In other applications where finger followers can facilitate complete loss of motion of the source of motion, such as cylinder rest, the adjustable support assembly engages the latch and lever when the latch is in the first latch position. , Can be adapted to allow the lever to pivot freely from the latch (ie, the latch and lever do not engage) when the latch is in the second latch position.

In one implementation, the finger follower with an adjustable support assembly is an adjustable latch or lever engagement adapted to move within the follower body to support the finger follower lever in at least one position. May include members. The lever engaging member or latch may cooperate with an actuating piston that can extend through the lateral hole in the lever engaging member. The piston obtains a first and second support surface that can provide two positively defined positions for the lever engaging member. In some applications, these two positions may correspond to the positively defined support positions of the finger follower lever. In other applications, only one of the latch positions may support the lever, and the other position of the latch may correspond to a lever that freely pivots to a position that is not engaged (lower) with the latch. .. The adjustable support assembly structure is fitted so that the lever does not load the working component when engaging the latch in a position other than the precisely defined position defined by the adjustable support assembly. And therefore avoid damage to the actuating components and / or levers due to partial engagement.

In one implementation, the finger follower is supported for movement with respect to the finger follower body and is substantially planar extending at an angle to the latch movement direction to engage the arcuate surface on the lever. Obtain a lever engaging member or latch having a lever engaging member surface or latch surface. The finger follower lever may have an arcuate surface adapted to be engaged by a planar lever engaging surface on the lever engaging member. Therefore, the lever engaging member surface and the lever surface are adapted to maintain a substantially similar contact shape when the lever and the lever engaging member surface are engaged. In addition to eliminating the possibility of partial engagement, these aspects provide improved durability and operation.

According to another implementation, the finger follower assembly can be applied to the valve mechanism environment of a single source of motion lost motion engine. In some applications, the adjustable support assembly may support the finger follower lever in at least two positions, at least one of which may be in the lost motion position. In other applications, the adjustable support assembly supports the finger follower lever in at least one position, where the finger follower lever is free to pivot so that the motion of the source of motion is not transmitted to the engine valve. It may be possible (as is possible in the case of cylinder rest applications). The urging assembly may include at least one elastic element disposed between at least one spring support on the follower body and at least one spring support on the lever. The movement limiting portion of the main body may limit the upward movement of the lever. One or more precisely defined lever support positions are performed by the interaction of the lever engaging member with the actuating piston to provide complete or partial transmission (or complete or) of valve motion via the lost motion finger follower. Partial loss) can be provided.

According to another embodiment, the finger follower may be equipped with an eccentric pivot mount that may provide adjustment of the position of the finger follower lever with respect to the follower body.

According to yet another aspect of the present disclosure, there is provided a method of controlling the operation of at least one valve of an internal combustion engine by using a valve mechanism component disposed between a motion source and a motion receiving component. The valve mechanism component includes a body, a lever adapted to pivot with respect to the body, and an adjustable support assembly to provide selective support to the lever. The actuation of the adjustable support assembly can be configured to take at least two operating states, the method in which the valve mechanism component is the first movement of the valve mechanism component from the source of motion to the motion receiving component. It is configured to take a first state that conveys the range, and when the valve mechanism component is in the first state, the engine is operated in the first operating mode, and the valve mechanism component is When the valve mechanism component is configured to take a second state of transmitting a second range of motion from the source of motion to the motion receiving component, and when the valve mechanism component is in the second state. Includes operating the valve mechanism component in a second mode of operation.

According to an example implementation, the adjustable support assembly provides three corresponding states or positions of the finger follower, each state or position may include a three-position latch that absorbs the corresponding range of motion. Motion sources such as cams have multiple lobes and can interact with finger followers to achieve different valve movements and thus different engine operating modes.

According to one example, the 3-position finger follower may be configured in a first state that supports engine operation in cylinder deactivation mode. The finger follower may further be configured with a second state that supports engine operation in the main event positive power mode. The figure follower can be further configured in a third state to support engine operation in auxiliary valve motion mode, including lost motion braking, late intake valve closure (LIVC), or early exhaust valve opening (EEVO). ) Can be included.

According to another example, the 3-position finger follower may be configured in a first state that supports engine operation in lost motion braking mode. The finger follower may be further configured in a second state to support engine operation in EEVO mode. The figure follower can be further configured in a third state to support engine operation in the main event positive power mode.

Other aspects and advantages of the present disclosure will be apparent to those of skill in the art from the detailed description below, and the above aspects should not be considered inclusive or restrictive. The general description above and the detailed description below are intended to provide examples of the inventive aspects of the present disclosure and are by no means limiting or binding the scope defined in the appended claims. Should not be interpreted as doing.

The above and other accompanying advantages and features of the invention will become apparent from the following detailed description, along with the accompanying drawings in which similar reference numerals represent similar elements throughout. The description and embodiments are intended as exemplary embodiments according to aspects of the present disclosure and are intended to be limited to the scope of the invention described in the claims herein. It will be understood that there is no such thing. In the description of the figures below, all illustrations relate to the features that are examples according to aspects of the present disclosure, unless otherwise noted.

It is a perspective view of an example of the switchable finger follower and engine valve mechanism environment of the prior art, which environment may be suitable for implementing aspects of the present disclosure. FIG. 1 is a cross-sectional view of the finger follower system of FIG. 1 in the “on” state. FIG. 1 is a cross-sectional view of the finger follower system of FIG. 1 in the “off” state. It is an assembly perspective view of an example of a finger follower assembly. It is an exploded perspective view of the example of the finger follower assembly of FIG. It is a detailed exploded perspective view of the adjustable support assembly of the finger follower. FIG. 6 is a vertical cross-sectional view of the finger follower assembly of FIG. 4 in a first state that may be in an "off" or "unlocked" state. FIG. 3 is a cross-sectional view of the finger follower assembly of FIG. 4 in the first state. FIG. 4 is a vertical cross-sectional view of the finger follower assembly of FIG. 4 in a second state, which may be in the "on" or "locked" state. 2 is a cross-sectional view of the finger follower assembly of FIG. 4 in the second state. FIG. 3 is an assembly perspective view of a finger follower assembly according to a second embodiment in an application as a lost motion device. 11 is an exploded perspective view of the lost motion finger follower assembly of FIG. FIG. 11 is a vertical cross-sectional view of the finger follower assembly of FIG. 11 in a first state, which may be a state in which some or all of the valve mechanism motion is lost. FIG. 11 is a vertical cross-sectional view of the finger follower assembly of FIG. 11 in a second state, where some or all of the movement of the valve mechanism can be transmitted. FIG. 6 is a vertical cross-sectional view of another embodiment of the finger follower assembly that allows the lever to pivot freely from the support assembly and facilitates complete loss of movement. It is a perspective view which shows the eccentric pivot mount. 16 is a cross-sectional view of the pivot mount of FIG. It is a cross-sectional view of the end of a three-position switchable finger follower. FIG. 18 shows an exemplary first implementation of the three-position embodiment. FIG. 18 shows an exemplary first implementation of the three-position embodiment. FIG. 18 shows an exemplary first implementation of the three-position embodiment. FIG. 18 shows an exemplary second implementation of the three-position embodiment. FIG. 3 shows a cross-sectional view of an alternative embodiment of a three-position valve mechanism component compatible with a Type III rocker configuration. The profiles of the three-position valve mechanism components for realizing various engine operation modes are shown. Illustrative cam profiles, lost motions, and valve lift motions that can be achieved in three different operating conditions using a three-position finger follower according to aspects of the present disclosure are shown. The steps of an exemplary method of performing cylinder deactivation, main event positive power, and auxiliary events such as lost motion braking, LIVEC, EEVO, etc. on an internal combustion engine using a 3-position finger follower are shown. The steps of an exemplary method of performing a main event positive power, EEVO, and lost motion braking using a 3-position finger follower in an internal combustion engine using a 3-position finger follower are shown.

FIG. 4 is a perspective view of an exemplary assembled switchable finger follower system 100 according to the present disclosure. FIG. 5 is an exploded perspective view of the same system. In particular, the switchable finger follower may include a body or housing 400 arranged to support or accommodate various other system components. The body 400 is adapted to contact or engage a pivot axis that may include an HLA from a motion transmission end or valve engagement end 410 adapted to contact or engage one or more engine valves. It can extend longitudinally to the pivotal end 420. The body 400 further includes a pair of arms 402 and 404 extending laterally longitudinally, from which a lever recess or pocket 406 may be defined. The arms 402 and 404 may include the valve engaging end 410 with the pivot pin receiving holes 403 and 405, respectively, to secure the lever pivot pin 412 therein. The pair of lateral roller followers 430 and 434 may be secured to the arms 402 and 404 via shafts 432 and 436, respectively. The lateral roller followers 430 and 434 are configured to receive valve actuated motion from a complementary valve actuated motion source, eg, a source similar to the lateral cam lobe 9 shown in FIG. Although the lateral followers are shown in roller form, the present disclosure needs to be limited in this regard as the lateral followers can be implemented, for example, as a flat follower contact area extending from the body 400. It is understood that there is no.

The body 400 may further support a lever 450 having a fixed end 452 that can be mounted pivotally with the follower body 400 and extending longitudinally to the free end 460. The fixed end of the lever 450 may be fixed to the lever pivot pin 412 fixed to the arms 402, 404 of the body 400.

The lever 450 has a shape that complements a recess or pocket 406 within the body 400, thereby providing nesting positioning within the body 400 and an overall compact finger follower configuration. The lever 450 can be formed as a precision single punched metal (ie, steel) component having a substantially concave shape with an integral outer wall 456 extending from the bottom wall 454 and the bottom wall 454. The central portion of the lever 450 is capable of supporting and accommodating motor receiving components associated with the lever. The motion receiving component can be a central roller follower 440 supported on a shaft 442 mounted on the lever 450. Alternatively, the motor-accepting component associated with the lever is adapted to be directly on or mounted on the lever and directly engage the valve mechanism component that cooperates with the source or source of motion. Can be a contact surface. A recess or notch 458 may be formed in the bottom wall 454 to accommodate the central roller follower 440. The free end 460 of the lever is arcuate or separate with an arcuate or otherwise curved end face 462 to selectively engage the adjustable support assembly 500 integrated into the body 400, as described. It may have a lever end wall 461 curved in the same manner. The end wall 461 may be extended and contoured to have a smooth transition with the bottom wall 454. The lever end wall 461 can extend between the reduced lateral dimensions between the opposing portions of the outer wall 456, thereby not only providing additional stability and strength, but also the operating end wall 461. The possibility of deformation can be reduced.

As will be appreciated, the central roller follower 440 may be configured to selectively receive valve actuated motion from a complementarily configured valve actuated motion source. For example, referring to the engine environment described above with respect to FIG. 1, the central roller follower 440 may receive a valve actuating motion from the central cam lobe, similar to the cam lobe 8 of FIG. As will be appreciated, according to aspects of the present disclosure, the finger follower configurations described herein are broader laterally and as compared to prior art systems such as those described above with respect to FIGS. 1-3. It has the advantage of allowing for a central follower dimension. This allows for a wider cam surface and thus, for example, the contact stress and wear between the cam and follower can be reduced.

Further referring to FIGS. 6-10, the pivot end 420 of the finger follower body 400 has a longitudinal hole 422 and lateral holes formed therein to accommodate the components of the adjustable support assembly 500. It may include a hole 424. The pivot end 420 is also in contact with and pressurized to a suitable pivot assembly such as a hydraulic rush adjuster with a post adapted to fit within a recess or pocket 426, as described further. It may include a recess or pocket 426, including a hydraulic passage 428 (FIG. 8) for delivering the hydraulic working fluid (oil) to the finger follower.

The adjustable support assembly 500 may include a lever engaging member or latch 510 and an actuating piston 530 associated with it. The lever engaging member or latch 510 may be disposed in a longitudinal hole 422 including a cylindrical guide surface 423 to support and facilitate the sliding movement of the lever engaging member or latch 510. The lever engaging member or latch 510 is approximately cylindrical including an outer cylindrical surface 512 and a substantially planar lever engaging surface 514 that may extend at an angle to the axis of the lever engaging member or latch 510. Can have a shape. The laterally actuated piston receiving hole 516 may extend through a lever engaging member or latch 510 to receive and cooperate with the actuating piston 530. Further, the lever engaging member or latch 510 is chamfered on each side to transition from the outer surface of the lever engaging member or latch 510 to the piston receiving hole 516 in order to provide smooth interaction with the surface of the piston 530. The surface 518 (FIG. 5) may be provided. Also, the chamfered surface 518 provides a reduction in the width of the transverse piston receiving hole 516, thereby providing the transverse hole 516 to engage the reduced diameter piston surface 532. It will be recognized that it eliminates the need for precise alignment with the piston 530.

The actuating piston 530 may include a first support surface 532 adapted to engage and support a lever engaging member or latch 510 in a first position within the longitudinal hole 422, which first position. , The lever 450 and the central follower 440 with respect to the body 400 may be unlocked, lowered, or retracted. The first support surface 532 can be a cylindrical surface having a first diameter. The actuating piston 530 may also include a second support surface 534 adapted to engage and support a lever engaging member or latch 510 in a second position within the longitudinal hole 422, the second position thereof. Can correspond to the locking, ascending, or unfolding position of the lever 450 and the central follower 440 with respect to the body 400. The second support surface is larger than the first diameter of the first support surface and substantially corresponds to the diameter of the lateral hole 424 of the main body 400 and substantially corresponds to the diameter of the laterally actuated piston receiving hole 516. It can be a cylindrical surface with a second diameter. Disposed between the first support surface 532 and the second support surface 534 may be a transition surface 536 on the actuating piston 530, wherein the transition surface 536 is a locking operation of the actuating piston. Medium, it can be generally tapered or conical, adapted to provide a smooth transition from the first support position to the second position of the lever engagement member. The transition surface 536 also disengages the actuating piston if it can be in an intermediate position between the fully retracted and fully deployed positions within the lateral hole 424, as described in more detail below. It is possible to easily return to the position.

Next, the operation of the adjustable support assembly 500 will be described. 7 and 8 show an exemplary switchable finger follower in the "unlocked" or off state, with the lever 450 at a lower position with respect to the body 400. The piston 530 is completely retracted into the lateral hole 424 and bottoms out on the end wall 425 of the lateral hole 424. An urging device such as a coil spring 533 may be disposed in the lateral hole 424 and engage with the spring seat 539 to urge the piston towards the retracted position. This position aligns the first support surface 532 of the actuating piston 530 with the lever engaging member or the lateral piston receiving hole 516 of the latch 510. The lever engaging member or latch 510 is retracted into the longitudinal hole such that the contact surface 514 is positioned along the first contact line to contact the lever end surface 462, with the first contact line being the lever. It may be in a lower position (ie, below the axis) on the surface 514 of the engaging member or latch 510. A spring holding cap 535 can be attached to the body 400 (ie, by press fitting or threading) to hold the spring 533 and piston 530 in the lateral hole 424.

As shown in FIG. 8, the pivot receiving pocket 426 of the body 400 may be hydraulically connected to the lateral hole 424 via the hydraulic passage 428. If the pressurized hydraulic fluid is not supplied to the first lateral hole through the passage 428, the urging element (not shown) urges the piston 530 to the left as shown in FIG. obtain. In this state, the reduced diameter surface 532 of the piston 530 is aligned with the lever engaging member or latch 510. Therefore, since the lever 450 is maintained at a lower position with respect to the body 400, the central roller follower 440 is similarly maintained at a lower position, thereby between the central roller follower 440 and its corresponding valve actuating source. Establish a rush. This rush space eliminates the valve actuation motion that would otherwise be applied to the central roller follower 440.

Further referring to FIGS. 9 and 10, according to aspects of the present disclosure, the adjustable support assembly 500 can be actuated to support the lever 450 in a second position with respect to the body 400. If the pressurized hydraulic fluid is provided, for example, from the passage of the supporting HLA (not shown) to the lateral hole 424 via the passage 428, the left urging applied to the piston 530 is the piston 530. Can be overcome such that the second support surface 536 is aligned with the lever engagement member or latch 510 and is displaced to a point that supports the engagement member or latch. It will be appreciated from the present disclosure that other hydraulic fluid actuation techniques may be utilized in place of or in addition to the hydraulic fluid actuation systems described by the examples herein. For example, pneumatic, electromagnetic, or purely mechanically interacting components can be utilized to provide the driving force for the operation of the described actuating pistons or pins 530. The transition surface 536 can move the lever engaging member 510 from the first latch position to the second latch position (to the right in FIG. 9) as the piston 530 moves. As a result, as best shown in FIG. 9, the lever end face 462 may, in this case, come into contact with the slide member surface 514 at a relatively high point on the slide member contact surface 506. Therefore, the lever 450 and the central roller follower 440 are supported in the second position, in this case higher than the position corresponding to the first (retracted) position of the lever support member 510, and the central roller follower 440 is the central roller. Any rush between the follower 440 and the corresponding valve actuating source can be absorbed. In this way, the valve actuating motion is applied to the central roller follower 440 and then transmitted to the body 400 by contact between the lever 450 and the slide member 510 and further contact between the slide member 510 and the body 400. Will be done. As recognized from the present disclosure, and as described in more detail in the context of lost motion, cylinder deactivation applications below, the first and second positions of the latch may define alternative states of the lever. More specifically, in the context of lost motion cylinder deactivation, the first position of the latch may be a "normal" operating state that facilitates the ascent of the lever to a higher position with respect to the follower body, and of the latch. The second position may be in the (retracted) "lost motion activation" operating state, where the lever does not engage the latch at all and may instead be lowered to a stationary position with respect to the follower body (ie, the movement of the lever). It is facilitated by a stop that defines the lower bound). In this state, the lever is in a lower position so that all valve motion otherwise transmitted by the source of motion can be "lost" or absorbed by the finger follower system.

According to one aspect of the present disclosure, the adjustable support assembly 500 provides an advantage in distributing the load applied by the lever 450 (indicated by the thick black arrow in FIG. 9). More specifically, the vertical component of the load is distributed to the body 400 via engagement between the outer surface 512 of the lever engaging member (also referred to herein as a latch) 510 and the inner surface of the longitudinal hole 422. (Indicated by the vertical dashed arrow). The horizontal component of the load (indicated by the horizontal dashed arrow) is distributed to the piston 530 via the lever engaging member or latch 510. As is recognized, the angle of the lever engaging surface 514 is selected so that most of the load is distributed over a wider area of the guide surface of the longitudinal hole 422 and a smaller component of the load is generated by the actuating piston 530. obtain. Further, it will be recognized that this load distribution occurs regardless of the position of the lever engaging member or latch 510 within the longitudinal hole 422. Moreover, due to the unique interaction of the lever end face 462 with the lever engaging member or the surface 514 of the latch 510, the possibility of partial engagement between these elements is effectively eliminated. Further, as shown, by providing a substantially arcuate shape to the lever end face 462, the contact stress between the lever engaging member 530 and the lever end face 462 can be controlled, i.e., the contact area between the elements. The size and shape of the lever can be kept substantially constant in all operating conditions and positions of the lever relative to the body, i.e., regardless of the position where the lever engaging member 530 engages the lever end face 462. The lever engaging member surface 514 and the lever end face 462 may be adapted to maintain substantially the same contact shape at all positions of the lever in contact with the lever engaging member surface 514. This improves durability and performance.

In addition, the unique interaction between the support surface of the piston 530 and the lever engagement member or latch 510 provides the lever 450 with two positively defined switched support positions that position, and thus actuation. The corresponding movement of the valve can be controlled very accurately. In addition, the forces involved in the interaction between the piston 530 and the lever engaging member 530 are reduced, thus improving durability and performance consistency. A further related advantage of the exemplary adjustable support assembly according to aspects of the present disclosure eliminates the possibility of excessive contact stress between the intermediate engagement position between the lever engagement member 530 and the lever 450. Such an intermediate position would be a position that is neither the first nor the second engaging position as described above. As will be appreciated, when the piston 530 is in the retracted position, only one position will be able to support the lever engaging member 530. If the lever engaging member is not in the first retracted position, no reaction force from the piston surface 532 is provided. Therefore, if the lever engaging member 530 stays in the second position or does not completely retract into the longitudinal hole 422 after the piston 530 retracts, the lever engaging member 530 comes to the first position. When the load of the motion source is transmitted to the lever 450, no reaction force is provided. In this way, the system avoids applying load forces when the working component is not in the first or second position. In other words, the lever support assembly 500 is adapted to provide support to the lever only in the first or second position. That is, when the piston 1530 is in the first position and the lever engaging member 1510 is in a position where it is not engaged with the piston, the system will ensure that the lever engaging member 1510 "floats" in the longitudinal hole 422. Allows and reaction force is not provided by the piston on the lever engaging member until properly seated against the piston 1530. Therefore, the adjustable support assembly is adapted to allow the lever to move to the first position when it is not in the first or second position. This arrangement eliminates damage to the support components and provides reliable and durable operation of the switchable finger follower.

11 to 13 show a second implementation that embodies the additional aspects of the present disclosure. This embodiment is an engine environment that uses a single source of motion, such as a cam, with one or more low lift events, such as auxiliary events where some lift can be lost, and more (or all) from the cam lobe. It can be useful as a lost motion device to provide high lift events such as combustion main events where the lift is transmitted to the engine valve. An exemplary lost motion engine environment is described, for example, in US Pat. No. 9,347,383, the subject matter of which is incorporated herein by reference in its entirety. As will be appreciated, in such applications, in the environment described above with respect to FIGS. 1-3, instead of the combination of the central 8 and the lateral cam lobes 9, a single cam profile with multiple lobes on it used.

FIG. 11 is a perspective view of an exemplary assembled lost motion finger follower system 1000 according to an aspect of the present disclosure. FIG. 12 is an exploded perspective view of the same exemplary system. The switchable finger follower may have the same general structure as the embodiments described above with respect to FIGS. 4-10. The structure and operation of the adjustable support assembly 1500, including the piston 1530, the lever engaging member 1510, and their interaction with the end face 1462, is similar to the mounts described above and may be applied to this embodiment. It is understood and does not need to be repeated. However, as will be appreciated, the structure of the body 1400 and lever 1450 can be modified to facilitate the functioning of the system in lost motion applications, as described below.

One modification may include the addition of an urging assembly adapted to work with the body 1400 and the lever 1450 to urge the lever 1450 towards an ascending or deploying position away from the body 1400. The body 1400 may include a pair of spring holding flanges 1402 and 1404 extending laterally. The respective elastic elements (eg, coil springs) 1422 and 1424 are held between the flanges and thus the lever 1450 and central roller follower 1440 towards the source of motion (ie, upward in FIGS. 11 and 12). Encourage.

In another modification, the movement limiting portion 1425 may be disposed on the pivot end 1430 of the body 1400 and limits the rotation of the lever 1450 away from the body 1400 by engaging with the top surface 1466 of the lever end wall 1461. Can be formed integrally with it. The movement stop 1425 is shown as an integral component of the body 1400, whereas the movement stop 1425 is as a separate component attached to or coupled to the body 1400 via another component. It will be understood that it can be implemented. Further, the movement stop portion 1425 may be provided with an adjustable function such as an adjusting screw that is screwed into the illustrated limiting portion and secured with a holding nut to allow the upper limit of movement of the lever 1450 to be adjusted.

As is known in the art, when a hydraulic rush regulator (HLA) is incorporated into a single source lost motion valve mechanism, the HLA expands during these operating conditions where valve actuation is lost. It is necessary to prevent, i.e., prevent the HLA from occupying the rush space deliberately provided for the selective loss of valve actuation. In the illustrated embodiment, this is such that the force exerted by these elements on the lever 1450 is greater than the force exhibited by the associated HLA as it expands and attempts to absorb the available rush. Achieved by the action of the selected elastic elements 1422 and 1424. In this way, the elastic elements 1422, 1424 apply sufficient load to the HLA to prevent unwanted expansion of the HLA. On the other hand, if the forces provided by the elastic elements 1422 and 1424 are uncontrolled and applied to the HLA, it can cause excessive compression or bleeddown of the HLA. Therefore, the movement limiting stop portion 1425 can limit the movement of the lever 1450 and, as a result, limit the force applied to the HLA associated with the elastic elements 1422, 1424. The travel distance of the lever 1450 made possible by the movement stop 1425 is lost when the HLA is operating to occupy the rush space in the valve mechanism when the lever 1450 is facing the movement stop 1425. It is preferred that the motion movement be controlled to be equal to the lost valve lift event. For example, if the movement stop 1425 allows an excessive stroke of the lever 1450, the lost motion operating state loses excessive motion and a relatively high lift valve event (eg, the main event) has excessive rush. The result is an undesired, lower valve lift and higher valve seating speed. Conversely, if the stop 1425 allows for an inadequate stroke of the lever 1450, an inadequate amount of rush space will be established during the lost motion operation and will nevertheless be lost valve actuation movement. A part of is transmitted to the engine valve by the finger follower. This can lead to undesired consequences such as valve lift and duration changes, and in some cases may add unwanted lift events when not desired. In embodiments where the movement stop 1425 is attached to the body 1400 (rather than being integrally formed with it), the movement stop 1425 is adjustable to allow precise control of the stroke of the lever 1450. Can be.

Yet another modification is not required in a single source environment where the finger follower system 1000 functions as a lost motion device as compared to the embodiments described above in connection with FIGS. 4-10. In some cases, it may include the elimination of lateral roller followers.

For lost motion applications, the adjustable support assembly 1500 provides at least two highly precisely controlled positions of the lever 1450 with respect to the finger follower body 1400, similar to the operation described above with respect to FIGS. 4-10. obtain. These two controlled positions may provide two levels of motion transmission from the source of motion to the actuation valve. The first position may correspond, for example, to the transmission of partial motion, and the second position may correspond to the transmission of complete motion. As recognized from the present disclosure, the embodiments described are "lost" or absorbed by the finger follower system of all valve motion that would otherwise be transmitted from the source (cam). Can be adapted to the lost motion application obtained. In such cases, the lever may have only one precisely defined engagement position with the latch 510, where the lever does not engage with the lever or the latch engages with the lever. A second position can be taken to support the lever at a position low enough that the valve lift is not transmitted from the source of motion. The non-engagement configuration of the lever can eliminate the need for precision in manufacturing, at least to define a second non-engagement position for the lever.

Referring to FIG. 13, the lever surface 1462 contacts the lever engagement member surface 1514 at a relatively low point, with the lever engagement member 1510 in the retracted position and supported on the smaller diameter of the piston 1530. do. The lever 1450 and roller follower 1440 are maintained in a lower position with respect to the body 1400, thereby establishing a rush between the roller follower 1440 and its corresponding valve actuated kinetic source. This rush space loses the relatively low lift valve actuation motion that would otherwise be applied to the central roller follower 1440, but the relatively high lift valve actuation motion is still received by the roller follower 1440 and fingered. It is transmitted to the follower body 1400 and finally to the valve engaged.

Further referring to FIG. 14, the piston is up to the point where its entire diameter portion completely occupies the lateral hole of the lever engaging member 1510, with the piston 1530 hydraulically actuated to overcome the spring-loaded force. You may move. Therefore, the lever engaging member 1510 is in the fully deployed position and the lever 1450 and follower 1440 are maintained in a relatively high position to absorb any rush between the follower 1440 and the valve actuating source. In this state, a relatively low lift valve actuation motion, as well as a relatively high lift valve actuation motion, is applied to the roller follower 1440, transmitted to the finger follower body 1400, and finally to the valve engaged thereby. Be transmitted.

In addition to the precisely controlled position of the lever 1450 with respect to the finger follower body 1400 and the precise control as a result of the lost motion capability provided by the finger follower system, the above configuration also provides intermediate positioning of the lever 1450. And thus provides the advantage of eliminating the intermediate transmission of valve motion. As described in detail above with respect to the operation of the adjustable support assembly 500 in the embodiments of FIGS. 4-10, the adjustable support assembly 1500 is due to the interaction of the piston 1530 with the lever engaging member 1510. It can be adapted to provide support at two defined positions.

FIG. 15 shows another embodiment according to aspects of the present disclosure, which may be useful in applications such as cylinder deactivation applications where complete loss of valve motion can be facilitated. In this embodiment, the lower lever positioning is such that the lever is free to pivot from the latch 2510 and is therefore lower relative to the follower body than was provided in the previously described embodiment ( Easily done by an adjustable support assembly 2500 that allows for a second) lever position. FIG. 15 shows the latch 2510 in the first position, with a larger diameter surface 2534 engaging with the lateral hole in the latch 2510 and supporting it in its indicated extension position, with the latch surface 2514 being the lever surface 2462. Engage with, thereby holding the lever 2450 in the indicated (first) position. This position may correspond to the "non-energized" state of the actuator piston 2530 (ie, the "normal latch" lever position), where the lever 2450 is positioned to transmit normal valve motion. According to aspects of this embodiment, when the piston 2530 is energized, the smaller diameter surface 2532 aligns with the lateral hole in the latch and the latch 2510 retracts (ie, moves up and left in FIG. 15). To make it possible. This position of the latch 2510 allows the lever 2450 to be completely free and pivot to a lower position that does not engage the latch 2510. Therefore, this configuration may be useful in applications such as cylinder deactivation applications where such a low lever position is required to completely eliminate valve motion.

16 and 17 show details of the pivot pin 1412 that can be used in any of the mounting embodiments described above. As shown, the pivot member 1412 comprises an eccentric shaft 920 formed therein. In particular, the axis of the shaft 920 is not aligned with the axis of the pivot member 912. Further, the eccentric shaft 920 is provided with a threaded mounting hole 922. As best shown in FIG. 17, the pivot member 912 may be supported by a body 400 with a lever 408 mounted to rotate on an eccentric shaft 920. A suitable fastener 1002 can be used to secure the assembly of the pivot member 912, lever 408, and body 400. By selectively rotating the pivot member 912, the position of the eccentric shaft 922 is relative to the body 1400 so that the pivot end of the lever 408 is similarly shifted upward or downward with respect to the body 1400. It may be moved. In this way, the pivot member 912 is used to adjust or control the position of the lever 1450 to work with different cam profiles to establish various rush settings, or to produce less accurate and less costly. The process can be enabled.

As will be appreciated, the geometry of the lever engaging member or latch 510, actuating piston 530, lever end face 462, and other surface interacting surfaces described herein, without departing from the spirit and scope of the invention. Can provide various geometric changes in. For example, the lever engaging member or latch 510 may have a curved or arcuate surface and the lever 450 may have a flat surface. Further, although described as a cylindrical element, the piston and lever engaging members may comprise a square or rectangular or other cross-sectional shape.

As a further example, the lever engaging member 530 is shown and described as operating under the control of mechanical interaction with the piston 530, which is then hydraulically controlled, to control the lever engaging member. It is understood that other configurations may be adopted. For example, the lever engaging member 530 may be urged to its unlocked or off state by an elastic element, and the hydraulic passage may be connected to the hole in which the lever engaging member 530 resides, resulting in a passage to the passage. The application of hydraulic fluid extends the lever engaging member 530 into its locked or on state, while the locked amount of hydraulic fluid in the hole of the slide member causes the lever engaging member 530 to reach its extended position. maintain. As another example, the lever contact surface 462 is shown to have an arcuate shape, but this is not a requirement and other surface configurations such as angled, semi-circular and the like can be similarly employed. Further, the configurations of the body 400 and the lever 450 can be reversed, i.e., the central body is provided with an outer movable arm, the movable arm having one or more similarly configured slide members as described above. It will be appreciated that it can be placed in the unlocked / off state or locked / on state to be used.

Here, with reference to FIG. 18, an actuating piston 1804 with various three-position embodiments is shown. As shown, piston 1804 includes, from right to left, a minimum diameter portion 1806, an intermediate diameter portion 1808, and a maximum diameter portion 1810, as shown in FIG. Further referring to FIG. 8, the embodiment of FIG. 18 is one or more hydraulic passages such as the hydraulic passage 428 of FIG. 8 and one or more springs or one or more such as the urging element 533 of FIG. Basis elements may be included, which may be used to control alignment of any of the piston portions 1806, 1808, 1810 with the slide member 1802 in a manner substantially similar to that described above with respect to FIG. can. For example, when hydraulic pressure is not applied to the left end side of the actuating piston 1804 (as shown in FIG. 18), the elastic element on the right end side of the piston 1804 causes the piston 1804 to index as far to the left as possible. Allows the smallest diameter portion 1806 to align with the slide member 1802. Through the application of the first pressure to the left end side of the piston 1804, the left urging force applied by the elastic element is the piston 1804 to the right so that the intermediate diameter portion 1808 of the piston 1804 aligns with the slide member 1802. Can be overcome to the extent that it is possible to be indexed to. When a second pressure higher than the first pressure is applied to the left end side of the piston 1804, the urging force of the elastic element is further overcome and the piston 1804 so that the maximum diameter portion 1810 of the piston 1804 aligns with the slide member 1802. Is further indexed to the right.

Thus, when the smallest diameter portion 1806 is aligned with the slide member 1802, the slide member 1802 can retract into its longitudinal hole to the maximum extent possible by the piston 1804 (maximum retracted state). On the other hand, when the maximum diameter portion 1810 is aligned with the slide member 1802, the slide member 1802 cannot (or can only retract to a minimum) retract into its longitudinal hole and is instead retracted by the piston 1804. Retained in an extended position, exiting the longitudinal hole to the maximum possible range (maximum extended state). Finally, when the intermediate diameter portion 1808 is aligned with the slide member 1802, the slide member 1802 retracts partially within its longitudinal hole, i.e., at a position between the maximum retracted state and the maximum extended state. Can be done. Various examples of such behavior are further shown in FIGS. 19-22.

19 to 21 show a first mounting embodiment of a three-position switchable finger follower in which the slide member 1802 includes stepped contact surfaces 1902, 1904. Further, the lever arm 408 comprises a contact surface 1906 configured to be complementary to any of the stepped contact surfaces 1902 and 1904. One or more elastic elements, such as a spring or other urging mechanism (eg, a hydraulic passage), can be provided to urge the slide member 1802 away from the lever arm to its maximum retracted state. In FIG. 19, the minimum diameter portion 1806 of the piston 1804 is aligned with the slide member 1802 so that the slide member 1802 can take its maximum retracted state. (Note that in FIGS. 19-21, the lateral holes of the slide member 1802 and the piston 1804 are omitted for clarity.) In this state, the slide member 1802 is in contact with the lever arm 408. The surface 1906 is retracted to the extent that it is prevented from coming into contact with the slide member 1802 at all. In this case, when the contact surface 1906 comes into contact with the lower stop portion 1908 of the main body 402, the downward deflection of the lever arm 408 is limited. The switchable finger follower thus configured may lose the maximum amount of motion applied to it, eg, correspond to an operating mode in which the corresponding cylinder is deactivated.

FIG. 19 also shows the motion source 1920 of the sample shown displaced from its normal operating position with respect to the finger follower for clarity. The source of motion 1920 can be a rotating cam with a main event lobe 1922, as well as two auxiliary lobes 1922 and 1924. It will be appreciated that the auxiliary lobes 1922 and 1924 can be positioned on the cam body at different rotational positions to achieve different lift profiles. The cam 1920 can interact with a follower roller, a finger follower, to give motion. The movement of the finger follower is transmitted or transmitted to the valve 1930.

The cam or motion source 1920 shown in FIG. 19 is combined with a three-state finger follower, for example, to selectively achieve main event valve lift, lost motion brake valve lift, and cylinder deactivation (without valve lift) operation. Can be used. It is recognized that alternative valve lift motion can be achieved with a suitable modification of the motion source profile (cam lobe) and a suitable modification of the motion transmission attributes of each state of the three-state finger follower. For example, if the CDA is not utilized in the third state and different lift events such as EEVO are desired, the source of motion may have different profiles, such as those shown and described below with respect to FIG. 24.

FIG. 20 shows a case where the intermediate diameter portion 1808 of the piston 1804 aligns with the slide member 1802 such that the slide member 1802 is larger than its maximum retracted state, smaller than its maximum extended state, and extends from the longitudinal hole. .. In this state, the slide member 1802 extends to such an extent as to allow contact between the first stepped contact surface 1902 of the slide member 1802 and the contact surface 1906 of the lever arm 408. The switchable finger follower of the illustration thus constructed is more than the applied motion below the first level (ie, the motion required to bring the contact surface 1906 into contact with the first stepped contact surface 1902. It also loses less motion), but the applied motion above the first level is transmitted. For example, in this mode of operation, the switchable finger follower transmits a relatively high valve lift, such as a main event lift, but may lose a relatively low lift, such as a brake or other auxiliary valve event.

FIG. 21 shows the case where the maximum portion 1110 of the piston 1804 is aligned with the slide member 1802 so that the slide member 1802 can take its maximum extended state. In this state, the slide member 1802 extends to such an extent as to allow contact between the second stepped contact surface 1904 of the slide member 1802 and the contact surface 1906 of the lever arm 408. The switchable finger follower of the illustration thus constructed is more than the applied motion below the second level (ie, the motion required to bring the contact surface 1906 into contact with the second stepped contact surface 1904). The applied motion above the second level is transmitted, although the second level in FIG. 21 is lower than the first level in the embodiment of FIG. 20. For example, in this mode of operation, the switchable finger follower can transmit a relatively low valve lift such as a brake or other auxiliary valve event, as well as a relatively high valve lift such as a main event lift.

In FIG. 22, the slide member 2202 comprises an angled contact surface 2206, and the lever arm 408 is in arcuate contact, for example, in a manner substantially similar to the embodiments shown in FIGS. 4-10. A second mounting embodiment of the three-position switchable finger follower provided with the surface 2208 is shown. FIG. 22 shows the lateral holes of the slide member 2202 and the piston 1804. Further, unlike the embodiments of FIGS. 19-21, an urging mechanism for urging the slide member 2202 away from the lever arm to its maximum retracted state is not required for the reasons described below.

FIG. 22 shows, in particular, the case where the intermediate diameter portion 1808 of the piston 1804 aligns with the slide member 2202 such that the slide member 2202 is larger than its maximum retracted state, smaller than its maximum extended state and extends from the longitudinal hole. Is shown. As a result, the lever arm contact surface 2208 engages with the slide member contact surface 2206 at a relatively low point on the slide member contact surface 2206. Similar to the embodiment shown in FIG. 20, the switchable finger follower thus configured has an applied motion below the first level (ie, a lever arm contact surface 2208 with a slide member contact surface). It loses less motion) than is required to contact the 2206, but the applied motion above the first level is transmitted. For example, in this mode of operation, the switchable finger follower transmits a relatively high valve lift, such as a main event lift, but may lose a relatively low lift, such as a brake or other auxiliary valve event.

On the other hand, when the minimum diameter portion 1806 of the piston 1804 is aligned with the slide member 2202, the slide member takes its maximum retracted state so that the lever arm contact surface 2208 does not engage with the slide member contact surface 2206 at all. Thereby, as in the embodiment of FIG. 19, it is possible for the lever arm 408 to lose the maximum amount of applied valve actuating motion. Further, when the maximum diameter portion 1110 of the piston 1804 aligns with the slide member 2202, the slide member is in its maximum extended state such that the lever arm contact surface 2208 engages a relatively high point on the slide member contact surface 2206. This allows the lever arm 408 to transmit a relatively low level of valve actuation motion, similar to the embodiment of FIG. Given the angular nature of the slide member contact surface 2206 and the arcuate nature of the lever arm contact surface 2208, any contact between the slide member contact surface 2206 and the lever arm contact surface 2208 is essentially the slide member 2202. Is urged to retract into its longitudinal hole. As a result, unlike the embodiments of FIGS. 19-21, no separate urging mechanism is required to urge the slide member into its longitudinal hole. Further, although different from the embodiment of FIGS. 19 to 21, the configuration of the slide member contact surface 2206 and the lever arm contact surface 2208 of FIG. 22 is a portion between the contact surfaces, as in the embodiment of FIGS. 4 to 14. It substantially avoids the possibility of targeted or incomplete engagement.

FIG. 23 shows an embodiment in which the three-position slide member 2308 is incorporated into a valve mechanism component other than the finger follower. For example, the valve mechanism component 2302 may include a central pivot type rocker arm or valve bridge. As shown, the actuator piston 2304 is disposed in a vertical hole 2303 formed in a valve mechanism component. The hydraulic channel 2306 is provided to communicate fluid with the vertical hole 2303. In one embodiment, the hydraulic channel 2306 supplies an unchecked low pressure hydraulic fluid to the vertical hole 2303 so that the actuator piston 2304 exits the vertical hole 2304 and is constantly urged. As further shown, the valve mechanism component 2302 includes a horizontal hole 2307 that intersects the vertical hole 2303. As shown, the slide member 2308 (similar to the slide member 1802 shown in FIGS. 19-21) is horizontal so that the stepped contact surface of the slide member 2308 can engage the end 2305 of the actuator piston 2304. It is disposed in the hole 2307. The piston 2310 (similar to the piston 1804 shown in FIG. 18) is provided to control the extension / retraction of the slide member 2308 in substantially the same manner as described above with respect to FIGS. 18-22.

When the actuator piston 2304 is placed under load (eg, as in the case of the valve opening actuation motion applied to the valve mechanism component 2302), the hydraulic fluid in the vertical hole 2303 flows back into the hydraulic channel 2306, which This allows the actuator piston 2304 to retract into the vertical hole 2303 until the end 2305 of the actuator piston 2304 touches one of the stepped surfaces of the slide member 2308 or reaches the bottom of the vertical hole 2303. In this latter case, i.e., if the slide member 2308 is positioned to avoid contact with the actuator piston 2304 (or to contact the actuator piston 2304 only at the lowest contact surface step). If the stroke length of the actuator piston 2304 provided is greater than the maximum valve actuating motion available, then all such valve actuating motion is lost. Conversely, if the slide member is positioned such that one of the steps of the higher contact surface engages the end 2305 of the actuator piston, the stroke length of the actuator piston 2304 may provide varying degrees of lost motion. Correspondingly restricted.

Although certain preferred embodiments have been presented and described, those skilled in the art will appreciate that changes and modifications can be made without departing from the teachings of the present invention. Accordingly, any modifications, variations, or equivalents of the above teachings are considered to be within the basic principles disclosed above and claimed herein. For example, the slide member 502 is described as operating under the control of mechanical interaction with the piston 504, which is then hydraulically controlled, but other configurations for controlling the slide member 502 may be employed. Understood. For example, the slide member 502 may be urged to its unlocked or off state by an elastic element, and the hydraulic passage may be connected to the hole in which the slide member 502 resides, resulting in application of the hydraulic fluid to the passage. Stretches the slide member 502 into its locked or on state, while a locked amount of hydraulic fluid in the hole of the slide member keeps the slide member 502 in its extended position. As another example, the lever arm contact surface 508 is shown to have an arcuate shape, but this is not a requirement and other surface configurations such as angled, semi-circular, etc. can be similarly employed. .. Further, the configurations of the body 402 and the lever arm 408 can be reversed, i.e., the central body is provided with an outer movable arm, the movable arm of which is one or more similarly configured slide members as described above. It is understood that can be placed in an unlocked / off state or a locked / on state using. In the same flow, the slide member 502 is not deployed in the body 402, but instead in the lever arm 408 so that the slide member contact surface 506 interacts with another contact surface on the body 402. Can be deployed in. It is also understood that the plurality of modes of operation resulting from the embodiments of FIGS. 18-22 can be extended to four or more states by using the additional intermediate diameter portion of the piston 1804. It is understood that in these embodiments where the slide member comprises a plurality of stepped contact surfaces, a single slide member can be replaced with a separate slide member that engages the lever arm at different positions.

FIG. 24 shows an exemplary finger follower and an exemplary engine operating mode lost motion profile that may correspond to the three positions or states of the three-position finger follower as described above. The curved portion represents the relative stroke length of the exemplary three-state finger follower, which is the range of cam (source) motion that can be absorbed by the finger follower before the finger follower transmits the cam motion to the valve. Is. In this figure, the stroke length (y-axis) is related to the position (x-axis) of the slide member 1802 (FIG. 19) or 2308 (FIG. 23). The first state represented by the curved portion 2402 and the corresponding first stroke length when the slide member 1802 is in the position shown in FIG. 21 absorbs the first (minimum) range of motion and into the valve. Lost motion brake (LMB) motion can be transmitted. The second state represented by the curved portion 2406 and the corresponding second stroke length greater than the first stroke length absorbs the second range of motion larger than the first absorbed range of motion and causes the EEVO motion. Can be transmitted to the valve. The third state, represented by the curved portion 2408 and the third stroke length greater than the first and second stroke lengths, absorbs a third range of motion larger than the first and second range of motion and into the valve. The main event (ME) movement can be transmitted.

Further referring to FIG. 25, this figure further shows how cam motion can be lost (or transmitted) to a valve by an exemplary finger follower. The cam profile 2502 may correspond to a cam similar to the cam 1920 shown in FIG. Profile 2502 may include a main event lift profile 2522, a first auxiliary lift profile 2524, and a second auxiliary lift profile 2526. Examples of the range of motion transmitted (lost) by the finger follower in three different states are represented by R1, R2, and R3. In this figure, the first state of the finger follower is represented by a line that coincides with the x-axis and the range of motion or stroke length (R1, in this case zero) absorbed by the finger follower. That is, in this state, all motion is transmitted by the finger follower. The dashed line (long / short) represents the second state of the finger follower and the corresponding absorbed second range of motion or stroke length (R2). As can be seen, in this state the movements of the auxiliary lobes 2524 and 526 may be hidden (lost) and only the movement of the main event lobe 2522 is transmitted. The dashed line above represents the third state of the finger follower and the third range of absorbed motion or stroke length (R3). In this state, the central peak portion of the main event profile 2522 can be transmitted. As will be appreciated, the cam profiles described above with reference to FIGS. 24 and 25 are merely examples and may be implemented in other configurations using other mechanisms without departing from the scope of the present disclosure.

In particular, from FIG. 25, for example, the stepwise increase in steps between the stepped contact surfaces 1902 and 1904 in FIG. 19 is shown as uniform (ie, steps of the same height), but with R3 in FIG. It will be recognized that the steps may be different, as represented by the difference in R2, the difference between R2 and R1. That is, the heights of the first step and the second step may be different and are not always the same.

In addition, it will be appreciated that the various engine operating modes achieved by the exemplary implementations of the present disclosure can be configured with appropriate variations in the height and number of cam lobes available. For example, cylinder deactivation (CDA) can be implemented as one of the modes of operation, in which case even the movement of the main event can be lost. Referring back to FIG. 24, in such implementations, CDA / main event / auxiliary event motion may be used to replace the LMB / EEVO / ME mode shown in FIG. More specifically, an auxiliary valve motion may occur when operating in the third portion 2408, a main event exhaust motion may occur in the second portion 2406, and an auxiliary motion may be added in the first flat portion 2402. (Lost motion brake / LIVC / EEVO, etc.).

FIG. 26 shows exemplary method steps that can be achieved according to aspects of the present disclosure. At 2602, the finger follower is configured in a first state / position in which the slide member 1802 (eg, FIGS. 18 and 19) is moved to its leftmost position and the finger follower does not transmit the lift from the cam 1920. At 2604, the engine operates in cylinder deactivation mode because all motion from the cam lobe is absorbed by the follower. At 2606, the finger follower may be configured in a second state / position, in which the slide member 1802 is shifted to the right (FIG. 19) to the second position (FIG. 20) and the finger follower cams. Transmits a second range of motion from. At 2608, the engine operates in the main event positive power operating mode. At 2610, the finger follower may be configured in a third position / position, in which state the slide member 1802 is further shifted to the right (FIG. 19) to a third position (FIG. 21). In step 2612, the engine operates in an auxiliary mode such as lost motion braking, late intake valve closing, or early exhaust valve opening.

FIG. 27 shows another exemplary method that can be achieved according to aspects of the present disclosure. At 2702, the finger follower is configured in a first state / position where the slide member 1802 (eg, FIGS. 18 and 19) is moved to its leftmost position and the finger follower transmits the main event lift from the cam 1920. To. Therefore, the first position in this case corresponds to the valve mechanism component (finger follower) that transmits only the highest lift (ie, main event) profile at the source of motion. At 2706, the finger follower may be configured in a second state / position, in which the slide member 1802 is shifted to the right (FIG. 19) to the second position (FIG. 20) and the finger follower cams. Transmits a second range of motion from. At 2608, the engine operates in EEVO operation. At 2710, the finger follower may be configured in a third position / position, in which state the slide member 1802 is further shifted to the right (FIG. 19) to a third position (FIG. 21). At step 2712, the engine operates in lost motion braking mode.

This implementation has been described with reference to specific exemplary embodiments, but without departing from the broader intent and scope of the invention as described in the claims, various modifications. And it will be clear that changes can be made to these embodiments. Therefore, the specification and drawings should be considered as exemplary rather than limiting.

Claims (16)

A method of controlling the movement of at least one valve of an internal combustion engine using a valve mechanism component disposed between a motion source and a motion receiving component, wherein the valve mechanism component is a main body and a main body. The valve mechanism component comprises a lever adapted to pivot with respect to the body and an adjustable support assembly for providing selective support to the lever, wherein the valve mechanism component is of the adjustable support assembly. Depending on the operation, it can be configured into at least two operating states, the method described above.
The valve mechanism component constitutes the valve mechanism component in a first state in which the first range of motion is transmitted from the motion source to the motion receiving component.
When the valve mechanism component is in the first state, the engine is operated in the first operation mode.
The valve mechanism component constitutes the valve mechanism component in a second state in which the second state of motion is transmitted from the motion source to the motion receiving component.
A method comprising operating the valve mechanism component in a second mode of operation when the valve mechanism component is in the second state. The method according to claim 1, wherein the first motion range of the valve mechanism component is a motion range in which motion is not transmitted from the motion source, and the first operation mode is a cylinder deactivation mode. The source of motion is configured to provide the main event motion to the at least one valve, and the second range of motion of the valve mechanism component is such that the principal event motion is from the source of motion to the motion receiving component. The method of claim 1, wherein the range of motion is such that it is transmitted. A step of configuring the valve mechanism component in a third state in which the valve mechanism component transmits a third range of motion from the motion source to the motion receiving component.
The method of claim 1, further comprising a step of operating the engine in a third mode of operation when the valve mechanism component is in the third state. The source of motion is configured to provide assistive motion to the at least one valve, and a third range of motion of the valve mechanism component is such that the assistive motion is transmitted from the source of motion to the motion receiving component. The method according to claim 4, which is a range of exercise such as that. The method of claim 5, wherein the assistive movement facilitates lost motion braking. The method of claim 5, wherein the assistive movement facilitates early opening of the exhaust valve. The method of claim 5, wherein the assistive movement facilitates late closure of the intake valve. The motion source is configured to provide a lost motion brake to the at least one valve, and the first range of motion of the valve mechanism component is such that the lost motion brake is from the motion source to the motion receiving component. The method of claim 1, wherein the range of motion is such that it is transmitted to. The kinetic source is configured to provide an early exhaust valve opening motion, and the second range of motion of the valve mechanism component is such that the early exhaust valve opening motion is transmitted from the kinetic source to the motion receiving component. The method according to claim 1, which is a range of exercise such as that. A step of constituting the valve mechanism component in a third state in which the valve mechanism component transmits a third range of motion from the motion source to the motion receiving component.
Further comprising the step of operating the engine in the third mode of operation when the valve mechanism component is in the third state.
The motion source is configured to provide the main event motion to the at least one valve, and the third range of motion of the valve mechanism component is such that the principal event motion is from the motion source to the motion receiving component. The method of claim 1, wherein the range of motion is such that it is transmitted. The method of claim 1, wherein the step constituting the valve mechanism component in the first state further comprises a step of activating a movable latch in the adjustable support assembly. 12. The method of claim 12, wherein the step of activating the movable latch further comprises a step of moving an actuating piston that cooperates with the movable latch. 13. The method of claim 13, wherein the step of moving the actuating piston further comprises hydraulically actuating the actuating piston. 4. The step of configuring the valve mechanism component into the first, second, and third states further comprises the step of activating a movable latch in the adjustable support assembly. The method described in. The step of configuring the valve mechanism component in the first state is a step of activating a movable latch in the adjustable support assembly to support the lever with a stepped engagement surface on the movable latch. The method according to claim 1, further comprising.

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