U.S. patent application number 12/611297 was filed with the patent office on 2010-05-06 for rocker shaft mounted engine brake.
This patent application is currently assigned to JACOBS VEHICLE SYSTEMS, INC.. Invention is credited to Zdenek S. Meistrick, ROBERT S. PERKINS.
Application Number | 20100108007 12/611297 |
Document ID | / |
Family ID | 43970302 |
Filed Date | 2010-05-06 |
United States Patent
Application |
20100108007 |
Kind Code |
A1 |
Meistrick; Zdenek S. ; et
al. |
May 6, 2010 |
ROCKER SHAFT MOUNTED ENGINE BRAKE
Abstract
A system for actuating an engine valve is disclosed. The system
may include a lost motion housing having two spaced collars
surrounding a rocker shaft. The lost motion housing may include an
internal hydraulic circuit connecting a hydraulic fluid supply
passage with an actuator piston. The system may include a means for
securing the lost motion housing in a fixed position relative to
the rocker shaft.
Inventors: |
Meistrick; Zdenek S.; (West
Granby, CT) ; PERKINS; ROBERT S.; (EAST GRANBY,
CT) |
Correspondence
Address: |
KELLEY DRYE & WARREN LLP
3050 K STREET, NW, SUITE 400
WASHINGTON
DC
20007
US
|
Assignee: |
JACOBS VEHICLE SYSTEMS,
INC.
BLOOMFIELD
CT
|
Family ID: |
43970302 |
Appl. No.: |
12/611297 |
Filed: |
November 3, 2009 |
Related U.S. Patent Documents
|
|
|
|
|
|
Application
Number |
Filing Date |
Patent Number |
|
|
12076173 |
Mar 14, 2008 |
|
|
|
12611297 |
|
|
|
|
60895318 |
Mar 16, 2007 |
|
|
|
Current U.S.
Class: |
123/90.46 |
Current CPC
Class: |
F01L 2305/00 20200501;
F01L 2001/186 20130101; F01L 1/08 20130101; F01L 13/065 20130101;
F01L 1/181 20130101; F02M 26/01 20160201; F01L 1/20 20130101; F01L
2800/10 20130101 |
Class at
Publication: |
123/90.46 |
International
Class: |
F01L 1/18 20060101
F01L001/18 |
Claims
1. A system for actuating an engine valve comprising: a rocker
shaft having a hydraulic fluid supply passage; a lost motion
housing having a collar surrounding the rocker shaft, an actuator
piston bore, and an internal hydraulic circuit extending from the
actuator piston bore to the hydraulic fluid supply passage; means
for securing the lost motion housing in a fixed position relative
to the rocker shaft; and an actuator piston slidably disposed in
the actuator piston bore.
2. The system of claim 1 wherein the hydraulic fluid supply passage
extends internally through the rocker shaft.
3. The system of claim 1 wherein the lost motion housing has two
collars surrounding the rocker shaft.
4. The system of claim 3 further comprising: a control valve bore
provided in the lost motion housing, said control valve bore
communicating with the internal hydraulic circuit; and a control
valve disposed in the control valve bore.
5. The system of claim 4 further comprising a check valve disposed
in the control valve.
6. The system of claim 5 wherein the means for securing is provided
on a side of the lost motion housing which is distal from the
actuator piston.
7. The system of claim 5 wherein the means for securing is provided
on a side of the lost motion housing which is proximal to the
actuator piston.
8. The system of claim 5 wherein the means for securing is provided
on both a side of the lost motion housing distal from the actuator
piston and a side of the lost motion housing proximal to the
actuator piston.
9. The system of claim 6 wherein the means for securing the lost
motion housing comprises a boss extending from said lost motion
housing collar and a bolt extending from said boss into an engine
component.
10. The system of claim 7 wherein the means for securing the lost
motion housing comprises a flange extending from said lost motion
housing proximal to the actuator piston and a bolt extending from
said flange into an engine component.
11. The system of claim 1 further comprising: a control valve bore
provided in the lost motion housing, said control valve bore
communicating with the internal hydraulic circuit; and a control
valve disposed in the control valve bore.
12. The system of claim 11 further comprising a check valve
disposed in the control valve.
13. The system of claim 1 wherein the means for securing is
provided on a side of the lost motion housing which is distal from
the actuator piston.
14. The system of claim 1 wherein the means for securing is
provided on a side of the lost motion housing which is proximal to
the actuator piston.
15. The system of claim 1 wherein the means for securing is
provided on both a side of the lost motion housing distal from the
actuator piston and a side of the lost motion housing proximal to
the actuator piston.
16. The system of claim 1 further comprising a solenoid valve
adapted to control the supply of hydraulic fluid to said hydraulic
fluid supply passage.
17. The system of claim 1 wherein the actuator piston further
comprises: a hollow interior; an adjustable depth lash adjustment
screw-plunger partially disposed in said hollow interior and
extending out of the top of the actuator piston bore, said
screw-plunger having a lower plunger end; a retaining collar
disposed in said hollow interior above said lower plunger end; and
a spring disposed between the retaining collar and the lower
plunger end.
Description
CROSS-REFERENCE TO RELATED APPLICATIONS
[0001] The present application relates to, is a continuation in
part of, and claims the priority of U.S. patent application Ser.
No. 12/076,173 filed Mar. 14, 2008 entitled "Engine Brake Having An
Articulated Rocker Arm And A Rocker Shaft Mounted Housing," which
relates to, and claims the priority of U.S. Provisional Patent
Application Ser. No. 60/895,318 filed Mar. 16, 2007, which is
entitled "Engine Brake Having an articulated Rocker Arm and a
Rocker Shaft Mount Housing."
FIELD OF THE INVENTION
[0002] The present invention relates to a system and method for
providing engine braking in an internal combustion engine.
BACKGROUND OF THE INVENTION
[0003] Internal combustion engines typically use either a
mechanical, electrical, or hydro-mechanical valve actuation system
to actuate the engine valves. These systems may include a
combination of camshafts, rocker arms and push rods that are driven
by the engine's crankshaft rotation. When a camshaft is used to
actuate the engine valves, the timing of the valve actuation may be
fixed by the size and location of the lobes on the camshaft.
[0004] For each 360 degree rotation of the camshaft, the engine
completes a full cycle made up of four strokes (i.e., expansion,
exhaust, intake, and compression). Both the intake and exhaust
valves may be closed, and remain closed, during most of the
expansion stroke wherein the piston is traveling away from the
cylinder head (i.e., the volume between the cylinder head and the
piston head is increasing). During positive power operation, fuel
is burned during the expansion stroke and positive power is
delivered by the engine. The expansion stroke ends at the bottom
dead center point, at which time the piston reverses direction and
the exhaust valve may be opened for a main exhaust event. A lobe on
the camshaft may be synchronized to open the exhaust valve for the
main exhaust event as the piston travels upward and forces
combustion gases out of the cylinder. Near the end of the exhaust
stroke, another lobe on the camshaft may open the intake valve for
the main intake event at which time the piston travels away from
the cylinder head. The intake valve closes and the intake stroke
ends when the piston is near bottom dead center. Both the intake
and exhaust valves are closed as the piston again travels upward
for the compression stroke.
[0005] The above-referenced main intake and main exhaust valve
events are required for positive power operation of an internal
combustion engine. Additional auxiliary valve events, while not
required, may be desirable. For example, it may be desirable to
actuate the intake and/or exhaust valves during positive power or
other engine operation modes for compression-release engine
braking, bleeder engine braking, exhaust gas recirculation (EGR),
or brake gas recirculation (BGR). FIG. 19 of co-pending application
Ser. No. 11/123,063 filed May 6, 2005, which is hereby incorporated
by reference, illustrates examples of a main exhaust event 600, and
auxiliary valve events, such as a compression-release engine
braking event 610, bleeder engine braking event 620, exhaust gas
recirculation event 630, and brake gas recirculation event 640,
which may be carried out by an exhaust valve using various
embodiments of the present invention to actuate exhaust valves for
main and auxiliary valve events.
[0006] With respect to auxiliary valve events, flow control of
exhaust gas through an internal combustion engine has been used in
order to provide vehicle engine braking. Generally, engine braking
systems may control the flow of exhaust gas to incorporate the
principles of compression-release type braking, exhaust gas
recirculation, exhaust pressure regulation, full cycle bleeder
and/or partial bleeder type braking.
[0007] During compression-release type engine braking, the exhaust
valves may be selectively opened to convert, at least temporarily,
a power producing internal combustion engine into a power absorbing
air compressor. As a piston travels upward during its compression
stroke, the gases that are trapped in the cylinder may be
compressed. The compressed gases may oppose the upward motion of
the piston. As the piston approaches the top dead center (TDC)
position, at least one exhaust valve may be opened to release the
compressed gases in the cylinder to the exhaust manifold,
preventing the energy stored in the compressed gases from being
returned to the engine on the subsequent expansion down-stroke. In
doing so, the engine may develop retarding power to help slow the
vehicle down. An example of a prior art compression release engine
brake is provided by the disclosure of the Cummins, U.S. Pat. No.
3,220,392 (November 1965), which is hereby incorporated by
reference.
[0008] During bleeder type engine braking, in addition to, and/or
in place of, the main exhaust valve event, which occurs during the
exhaust stroke of the piston, the exhaust valve(s) may be held
slightly open during remaining three engine cycles (full-cycle
bleeder brake) or during a portion of the remaining three engine
cycles (partial-cycle bleeder brake). The bleeding of cylinder
gases in and out of the cylinder may act to retard the engine.
Usually, the initial opening of the braking valve(s) in a bleeder
braking operation is in advance of the compression TDC (i.e., early
valve actuation) and then lift is held constant for a period of
time. As such, a bleeder type engine brake may require lower force
to actuate the valve(s) due to early valve actuation, and generate
less noise due to continuous bleeding instead of the rapid
blow-down of a compression-release type brake.
[0009] Exhaust gas recirculation (EGR) systems may allow a portion
of the exhaust gases to flow back into the engine cylinder during
positive power operation. EGR may be used to reduce the amount of
NO.sub.x created by the engine during positive power operations. An
EGR system can also be used to control the pressure and temperature
in the exhaust manifold and engine cylinder during engine braking
cycles. Generally, there are two types of EGR systems, internal and
external. External EGR systems recirculate exhaust gases back into
the engine cylinder through an intake valve(s). Internal EGR
systems recirculate exhaust gases back into the engine cylinder
through an exhaust valve(s). Embodiments of the present invention
primarily concern internal EGR systems.
[0010] Brake gas recirculation (BGR) systems may allow a portion of
the exhaust gases to flow back into the engine cylinder during
engine braking operation. Recirculation of exhaust gases back into
the engine cylinder during the intake and/or early compression
stroke, for example, may increase the mass of gases in the cylinder
that are available for compression-release braking. As a result,
BGR may increase the braking effect realized from the braking
event.
SUMMARY OF THE INVENTION
[0011] Applicants have developed an innovative system for actuating
an engine valve comprising: a rocker shaft having a hydraulic fluid
supply passage; a lost motion housing having a collar surrounding
the rocker shaft, an actuator piston bore, and an internal
hydraulic circuit extending from the actuator piston bore to the
hydraulic fluid supply passage; means for securing the lost motion
housing in a fixed position relative to the rocker shaft; and an
actuator piston slidably disposed in the actuator piston bore. In
the foregoing system, the hydraulic fluid supply passage extends
internally through the rocker shaft. Further, the lost motion
housing may have two collars surrounding the rocker shaft. Still
further, a control valve bore may be provided in the lost motion
housing, wherein said control valve bore communicates with the
internal hydraulic circuit and a control valve is disposed in the
control valve bore. Still further, a check valve may be disposed in
the control valve. Still further, the means for securing may be
provided on a side of the lost motion housing which is distal from
the actuator piston, on a side of the lost motion housing which is
proximal to the actuator piston, or on both the side of the lost
motion housing distal from the actuator piston and the side of the
lost motion housing proximal to the actuator piston. Still further,
the means for securing the lost motion housing may comprise a boss
extending from the lost motion housing collar and a bolt extending
from the boss into an engine component. Still further, the means
for securing the lost motion housing may comprise a flange
extending from the lost motion housing proximal to the actuator
piston and a bolt extending from said flange into an engine
component. Still further, the system may further comprise a
solenoid valve adapted to control the supply of hydraulic fluid to
said hydraulic fluid supply passage.
[0012] It is to be understood that both the foregoing general
description and the following detailed description are exemplary
and explanatory only, and are not restrictive of the invention as
claimed. The accompanying drawings, which are incorporated herein
by reference, and which constitute a part of this specification,
illustrate certain embodiments of the invention and, together with
the detailed description, serve to explain the principles of the
present invention.
BRIEF DESCRIPTION OF THE DRAWINGS
[0013] In order to assist the understanding of this invention,
reference will now be made to the appended drawings, in which like
reference characters refer to like elements. The drawings are
exemplary only, and should not be construed as limiting the
invention.
[0014] FIG. 1 is a pictorial view of an engine brake system having
an articulated rocker arm and a rocker shaft mounted housing for
master and slave pistons constructed in accordance with a first
embodiment of the present invention and disposed in an internal
combustion engine.
[0015] FIG. 2 is an overhead exploded pictorial view of an engine
brake system having an articulated rocker arm, rocker shaft mounted
housing, and a rocker arm return spring in accordance with the
first embodiment of the present invention.
[0016] FIG. 3 is an overhead exploded pictorial view of the
underside of the engine brake system shown in FIG. 2 as arranged in
accordance with the first embodiment of the present invention.
[0017] FIG. 4 is a cross-sectional side view of a rocker shaft
mounted housing of FIGS. 2 and 3 which shows the master and slave
pistons arranged in accordance with the first embodiment of the
present invention.
[0018] FIG. 5 is a second cross-sectional side view of the rocker
shaft mounted housing of FIGS. 2 and 3 which shows the control
valve in hydraulic communication with the rocker shaft and the
master and slave pistons as arranged in accordance with the first
embodiment of the present invention.
[0019] FIG. 6 is a cross-sectional front view of the rocker shaft
mounted housing of FIGS. 2 and 3 showing the control valve and the
slave piston as arranged in accordance with the first embodiment of
the present invention.
[0020] FIG. 7 is a cross-sectional side view of the engine brake
system of FIGS. 2 and 3 showing the articulated rocker arm, rocker
shaft mounted housing, and cam lobe as arranged in accordance with
the first embodiment of the present invention when the engine brake
system is turned off.
[0021] FIG. 8 is a cross-sectional side view of the engine brake
system of FIGS. 2 and 3 showing the articulated rocker arm, rocker
shaft mounted housing, and cam lobe as arranged in accordance with
the first embodiment of the present invention when the engine brake
system is turned on and rocker arm is contacting the cam base
circle.
[0022] FIG. 9 is a cross-sectional side view of the engine brake
system of FIGS. 2 and 3 showing the articulated rocker arm, rocker
shaft mounted housing, and cam lobe as arranged in accordance with
the first embodiment of the present invention when the engine brake
system is turned on and the rocker arm is contacting the cam
compression-release bump.
[0023] FIG. 10 is a cross-sectional side view of an engine brake
system showing the articulated rocker arm, rocker shaft mounted
housing, and cam lobe as arranged in accordance with a second
embodiment of the present invention when the engine brake system is
turned off.
[0024] FIG. 11 is an exploded pictorial view of an engine brake
system having an articulated rocker arm, rocker shaft mounted
housing, and a rocker arm return spring in accordance with the
second embodiment of the present invention.
[0025] FIG. 12 is a cross-sectional side view of the engine brake
system of FIGS. 2 and 3 showing the oil passage schematic between
the engine oil supply passage, solenoid valve and rocker shaft.
[0026] FIG. 13 is an overhead pictorial view of a valve actuation
system that may be used for bleeder braking in particular, having a
rocker shaft mounted housing in accordance with a second embodiment
of the present invention.
[0027] FIG. 14 is a pictorial view of the underside of the valve
actuation system shown in FIG. 13 as arranged in accordance with
the second embodiment of the present invention.
[0028] FIG. 15 is a cross-sectional side view of a rocker shaft
mounted housing of FIGS. 13 and 14 which shows an alternative or
additional flange for securing the rocker shaft mounted housing in
a fixed position in accordance with an alternative embodiment of
the present invention.
[0029] FIG. 16 is a second cross-sectional side view of the rocker
shaft mounted housing of FIGS. 13 and 14 which shows the control
valve in hydraulic communication with the rocker shaft and the
actuator piston as arranged in accordance with the second
embodiment of the present invention.
[0030] FIG. 17 is a cross-sectional front view of the rocker shaft
mounted housing of FIGS. 13 and 14 showing the control valve and
the actuator piston as arranged in accordance with the second
embodiment of the present invention.
[0031] FIG. 18 is a cross-sectional side view of the valve
actuation system of FIGS. 13 and 14 showing the rocker shaft
mounted housing and actuator piston as arranged in accordance with
the second embodiment of the present invention when the actuator
piston is separated by a lash space from the sliding pin/engine
valve.
[0032] FIG. 19 is a cross-sectional side view of the valve
actuation system of FIGS. 13 and 14 showing the rocker shaft
mounted housing and actuator piston as arranged in accordance with
the second embodiment of the present invention when the system is
turned on and the actuator piston has actuated the engine
valve.
[0033] FIG. 20 is a cross-sectional side view of the valve
actuation system of FIGS. 13 and 14 illustrating control of
hydraulic fluid supply by a solenoid valve.
[0034] FIG. 21 is a cross-sectional side view of a valve bridge
disposed between an actuator piston and an engine valve in
accordance with an alternative embodiment of the present
invention.
[0035] FIG. 22 is a cross-sectional view of an alternative actuator
piston in accordance with an alternative embodiment of the present
invention.
DETAILED DESCRIPTION OF EMBODIMENTS OF THE INVENTION
[0036] Reference will now be made in detail to a first embodiment
of the present invention, an example of which is illustrated in the
accompanying drawings. With reference to FIG. 1, a system 50 for
actuating engine valves arranged in accordance with a first
embodiment of the present invention is shown. FIGS. 2-9 show
different views of the system shown in FIG. 1 and/or its
components. The system 50 may include a cam 100, an articulated
half rocker arm 200, a brake housing 300, a rocker shaft 400, and a
solenoid valve 500. The rocker arm 200 may be biased away from (or
alternatively towards) the cam 100 by a return spring 210 (see also
FIG. 11). The brake housing may be secured in position by a
anti-rotation bolt 310.
[0037] With reference to FIGS. 2 and 3, the rocker arm 200 may
further include a cam roller 220, a lug 230, and a central collar
240. The rocker arm return spring 210 may bias the rocker arm 200
towards the brake housing 300 such that the lug 230 contacts the
master piston 340. The brake housing 300 may further include an
anti-rotation bolt boss 312, a control valve 320, a master piston
340, a slave piston 350 and rocker shaft collars 360 and 362. A
slave piston return spring 352 may bias the slave piston 350 up
into a slave piston bore formed in the brake housing 300.
[0038] With reference to FIG. 4, the rocker shaft collars 360 and
362 of the brake housing 300 may be mounted on the rocker shaft
400. The brake housing may be secured in a fixed position relative
to the rocker shaft 400 by the anti-rotation bolt 310 (not shown).
The brake housing 300 may include a master piston 340 slidably
disposed in a master piston bore 302 and a slave piston 350
slidably disposed in a slave piston bore 304. A master-slave
hydraulic fluid passage 306 may extend between the master piston
bore 302 and the slave piston bore 304. The slave piston return
spring 352 may bias the slave piston 350 upward and against a slave
piston lash adjustment screw 354 which extends into the slave
piston bore 304. The rocker shaft 400 may include a first hydraulic
passage 410 adapted to provide lower pressure hydraulic fluid to
the rocker arm 200 (not shown in FIG. 4) for lubrication purposes.
The rocker shaft 400 may also include a second hydraulic passage
420, the purpose of which is explained in connection with FIG.
5.
[0039] With reference to FIG. 5, adjacent to the slave piston 350
(shown in FIG. 4) the brake housing 300 may further include control
valve 320. The control valve 320 may fill the master and slave
bores with hydraulic fluid when low pressure hydraulic fluid is
supplied to the lower portion of the control valve via a supply
passage 308. A connection hydraulic passage 422 provided in the
rocker shaft 400 may extend between the second hydraulic passage
420 and the supply passage 308 provided in the brake housing 300.
As a result, hydraulic fluid may be supplied to the control valve,
and the master and slave bores, by the selective supply of low
pressure hydraulic fluid in the second hydraulic passage 420.
[0040] A front cross-sectional view of the brake housing 300 is
shown in FIG. 6. With reference to FIG. 6, the control valve 320 is
shown in a "brake off" position during which the control valve body
322 is biased into its lower most position by the control valve
spring 326. When the brake is turned on, hydraulic fluid from the
second hydraulic passage 420 in the rocker shaft 400 (shown in FIG.
5) may be supplied to the lower portion of the control valve body
322. The supply of hydraulic fluid may cause the control valve body
322 to move upward until the annular opening provided in the
mid-portion of the control valve body registers with the slave bore
supply passage 309. The hydraulic fluid pressure applied to the
lower portion of the control valve 320 may be sufficient to push
the check valve 324 open so that hydraulic fluid flows into the
slave piston bore 304 via the slave bore supply passage 309. With
renewed reference to FIG. 4, the hydraulic fluid may further flow
from the slave piston bore 304 through the master-slave hydraulic
fluid passage 306 into the master piston bore 302. While the brake
is in a "brake on" position, hydraulic fluid may be supplied freely
to the master-slave piston circuit by the control valve 320, while
the check valve 324 within the control valve prevents the reverse
flow of fluid. As a result, the master-slave hydraulic circuit in
the brake housing 300 may experience high hydraulic fluid pressures
without substantial back flow of hydraulic fluid.
[0041] The brake may be returned to the "brake off" position shown
in FIG. 6 by reducing the hydraulic fluid pressure, preferably by
evacuating the hydraulic fluid, applied to the lower portion of the
control valve 320. When this happens, the control valve body 322
may slide downward until the slave bore supply passage 309 is
exposed to the control valve bore 328, thereby allowing the
hydraulic fluid in the master-slave hydraulic circuit to escape.
The selective supply of hydraulic fluid to the control valve 320
may be controlled by the solenoid 500 shown in FIG. 1. Alternative
placements of the solenoid 500 are considered within the scope of
the present invention.
[0042] The arrangement of the various elements of the system 50
when the engine brake is in a "brake off" position is shown in FIG.
7. With reference to FIG. 7, the cam lobe 100 is illustrated as
having two valve actuation bumps. A first cam bump 102 may provide
a compression-release valve actuation event and a second cam bump
104 may provide a brake gas recirculation (BGR) valve actuation
event. Alternative cam lobes with more, less, or different cam
bumps are contemplated as being within the scope of the present
invention.
[0043] The system 50 is positioned adjacent to an engine valve,
such as an exhaust valve 600. The system 50 may actuate the exhaust
valve 600 through a sliding pin 620 that extends through a valve
bridge 610. Use of such a sliding pin and valve bridge arrangement
may permit a separate valve actuation system to actuate multiple
engine valves for positive power operation and a single engine
valve 600 for non-positive power operation, such as engine
braking.
[0044] With continued reference to FIG. 7, when the brake is in a
"brake off" position, hydraulic fluid pressure in the second
hydraulic passage 420 is reduced or eliminated. As a result, there
is no hydraulic fluid pressure maintained in the master-slave
hydraulic fluid circuit connecting the master piston 340 and the
slave piston 350. Accordingly, the bias of the slave piston return
spring 352 may be sufficient to push the slave piston 350 all the
way into the slave piston bore against the lash adjustment screw
354. Furthermore, the bias of the rocker arm return spring 210 may
be sufficient to rotate the rocker arm 200 such that the rocker arm
lug 230 pushes the master piston 340 all the way into the master
piston bore. The rotation of the rocker arm 200 in this manner may
create a lash space 106 between the cam roller 220 and the cam lobe
100. The lash space 106 may be designed to have a magnitude x that
is as great or greater than the height of the cam bumps 102 and
104. Thus, when the system 50 is in a "brake off" position, the cam
bumps 102 and 104 may not have any effect on the rocker arm 200 or
the master and slave pistons 340 and 350.
[0045] The arrangement of the various elements of the system 50
when the engine brake is in a "brake on" position is shown in FIG.
8. With reference to FIG. 8, when the brake is turned "on,"
hydraulic fluid is supplied through the second hydraulic passage
420 to the control valve 320 (not shown) and the master-piston
hydraulic circuit in the brake housing. When the cam lobe 100 is at
base circle, as shown in FIG. 8, the hydraulic fluid pressure in
the master-slave hydraulic fluid circuit connecting the master
piston 340 and the slave piston 350 may push the master piston 340
out of its bore, overcoming the bias of the rocker arm return
spring 210 and rotating the rocker arm 200 backwards until the cam
roller 220 contacts the cam lobe 100. As a result, the lash space
106 may be eliminated. At this time (cam lobe at base circle), the
hydraulic pressure in the master-slave hydraulic circuit is not
sufficient, however, overcome the bias of the slave piston return
spring 352 and push the slave piston 350 out of the slave piston
bore.
[0046] With reference to FIG. 9, when the cam roller 220 encounters
the cam bump 102 (and 104), the rocker arm 200 is rotated slightly
clockwise. Rotation of the rocker arm 200 may push the master
piston 340 into the master piston bore thereby displacing hydraulic
fluid through the master-slave hydraulic fluid passage 306 and into
the slave piston bore. As a result, the bias of the slave piston
return spring 352 is overcome and the slave piston 350 may be
displaced downward against the sliding pin 620, which in turn, may
actuate the exhaust valve 600 for a compression-release event or
some alternative valve actuation event.
[0047] An alternative embodiment of the present invention is shown
in FIGS. 10 and 11. With reference to FIGS. 10 and 11, the rocker
arm return spring 210 may be provided in the form of a coil spring
as opposed to a mouse-trap type spring. Furthermore, the return
spring 210 may extend between an overhead element 212 and a rear
portion of the rocker arm 200 such that the rocker arm is biased
into continual contact with the cam lobe 100 when the system is in
a "brake off" position, as shown in FIG. 10. As a result, instead
of creating a lash space between the cam lobe 100 and the cam
roller 220 when the brake is off, a lash space 202 may be created
between the rocker arm lug 230 and the master piston 340.
[0048] With reference to FIG. 12, the communication between an
engine oil supply passage 430 and the first and second hydraulic
passages 410 and 420 are shown. The solenoid 500 may be disposed
between the engine oil supply passage 430 and the rocker shaft
400.
[0049] With reference to FIGS. 13 and 14, in a second embodiment of
the present invention, the rocker arm and master piston may be
eliminated. The valve actuation system housing 1300 may include an
anti-rotation bolt boss 1312, a control valve 1320, an actuator
piston 1350 and rocker shaft collars 1360 and 1362. The rocker
shaft collars may surround the rocker shaft providing a means for
securely fixing the housing 1300 in a fixed and compact position
relative to the engine valves to be actuated.
[0050] With reference to FIG. 15, the rocker shaft collars 1360 and
1362 of the housing 1300 may be mounted on the rocker shaft 1400.
The housing may be secured in a fixed position relative to the
rocker shaft 1400 by a first anti-rotation bolt 1310 (not shown)
that extends through the anti-rotation bolt boss 1312 and/or by a
second anti-rotation bolt 1314 that extends through an
anti-rotation flange 1316. The anti-rotation boss 1312 may be
provided distal from the actuator piston 1350 and the anti-rotation
flange 1316 may be provided proximal to the actuator piston. The
housing 1300 may include an actuator piston 1350 slidably disposed
in an actuator piston bore 1304. An internal hydraulic circuit may
include passage 1306 and passage 1308 (shown in FIG. 16). An
actuator piston lash adjustment screw 1354 may extend into the
actuator piston bore 1304 and provide an upper stop against which
the actuator piston 1350 may seat. The rocker shaft 1400 may
include a hydraulic fluid supply passage 1420, the purpose of which
is explained in connection with FIG. 16.
[0051] With reference to FIG. 16, adjacent to the actuator piston
1350 (shown in FIG. 15) the housing 1300 may further include a
control valve 1320. The control valve 1320 may fill the passage
1306 of the internal hydraulic circuit with hydraulic fluid when
low pressure hydraulic fluid is supplied to the lower portion of
the control valve via a passage 1308 of the internal hydraulic
circuit. A connection hydraulic passage 1422 provided in the rocker
shaft 1400 may extend between the hydraulic fluid supply passage
1420 and the passage 1308 provided in the housing 1300. As a
result, hydraulic fluid may be supplied to the control valve and
the actuator piston bores by the selective supply of low pressure
hydraulic fluid in the hydraulic fluid supply passage 1420.
[0052] A front cross-sectional view of the system is shown in FIG.
17. With reference to FIG. 17, the control valve 1320 is shown in a
"actuator off" position during which the control valve body 1322 is
biased into its lower most position by the control valve spring
1326. When the system is turned on, hydraulic fluid from the
hydraulic fluid supply passage 1420 in the rocker shaft 1400 (shown
in FIG. 16) may be supplied to the lower portion of the control
valve body 1322. The supply of hydraulic fluid may cause the
control valve body 1322 to move upward until the annular opening
provided in the mid-portion of the control valve body registers
with the passage 1306. The hydraulic fluid pressure applied to the
lower portion of the control valve 1320 may be sufficient to push
the check valve 1324 open so that hydraulic fluid flows into the
actuator piston bore 1304 via the passage 1306. While the system is
in an "actuator on" position, hydraulic fluid may be supplied
freely to the internal hydraulic circuit by the control valve 1320,
while the check valve 1324 within the control valve prevents the
reverse flow of fluid. As a result, the internal hydraulic circuit
in the housing 1300 may experience high hydraulic fluid pressures
without substantial back flow of hydraulic fluid.
[0053] The system may be returned to the "actuator off" position
shown in FIG. 17 by reducing the hydraulic fluid pressure in the
hydraulic fluid supply passage 1420, and preferably by evacuating
the hydraulic fluid applied to the lower portion of the control
valve 1320. When this happens, the control valve body 1322 may
slide downward until the passage 1306 is exposed to the control
valve bore 1328, thereby allowing the hydraulic fluid in the
internal hydraulic circuit to escape. The selective supply of
hydraulic fluid to the control valve 1320 may be controlled by the
solenoid 1500 shown in FIG. 20. Alternative placements of the
solenoid 1500 are considered within the scope of the present
invention.
[0054] The arrangement of the various elements of the system when
the engine valve actuator is in an "actuator off" position is shown
in FIG. 18. With reference to FIG. 18, the system is positioned
adjacent to an engine valve, such as an exhaust valve 1600. The
system may actuate the exhaust valve 1600 through a sliding pin
1620 that extends through a valve bridge 1610. Use of such a
sliding pin and valve bridge arrangement may permit a separate
valve actuation system to actuate multiple engine valves for
positive power operation and a single engine valve 1600 for
non-positive power operation, such as engine braking. With
continued reference to FIG. 18, when the system is in an "actuator
off" position, hydraulic fluid pressure in the hydraulic fluid
supply passage 1420 is reduced or eliminated. As a result, there is
no hydraulic fluid pressure maintained in the internal hydraulic
fluid circuit connected to the actuator piston 1350. As a result,
the actuator piston 1350 may rest against but not actuate the
sliding pin 1620. Thus, when the system is in an "actuator off"
position, the actuator piston may not provide any valve actuation
motion to the engine valve.
[0055] The arrangement of the various elements of the system when
it is in an "actuator on" position is shown in FIG. 19. With
reference to FIG. 19, when the system is turned "on," hydraulic
fluid is supplied through the hydraulic passage 1420 to the control
valve 1320 (not shown). Hydraulic fluid pressure in the passage
1306 may push the actuator piston 1350 out of its bore so that if
it is not already, it does contact the sliding pin 1620. At this
time the hydraulic pressure in the internal hydraulic circuit may
not be sufficient, however, to overcome the bias of the engine
valve 1600 spring 1602. When the valve bridge 1610 is moved
downward for main exhaust valve actuation event, for example, the
low pressure hydraulic fluid in the actuator piston bore 1304 may
push the actuator piston 1350 and the sliding pin 1620 downward so
that they follow the valve bridge until the actuator piston reaches
its maximum downward displacement. As the valve bridge 1610 returns
upward at the conclusion of the main exhaust event, the hydraulic
fluid in the passage 1306 may become highly pressurized so that the
actuator piston 1350 holds the exhaust valve 1600 open for an
engine valve event, such as a bleeder braking event. The actuator
piston 1350 may continue to hold the exhaust valve 1600 open until
the control valve 1320 releases the hydraulic fluid pressure in the
passage 1306. It is appreciated that the valve actuation system may
be used for intake and auxiliary engine valve actuation in addition
to exhaust valve actuation.
[0056] With reference to FIG. 20, the communication between an
engine hydraulic fluid supply passage 1430 and the hydraulic fluid
supply passage 1420 is shown. The solenoid valve 1500 may be
disposed between the engine hydraulic fluid supply passage 1430 and
the hydraulic fluid supply passage 1420 in the rocker shaft 1400.
The solenoid valve 1500 may be provided adjacent to the rocker
shaft mounted engine brake system on, for example, a rocker shaft
pedestal.
[0057] With reference to FIG. 21, in an alternative embodiment of
the system shown in FIGS. 13-20, the actuator piston 1350 may act
directly on an engine valve 1600 or on an engine valve bridge 1610
instead of acting on a sliding pin.
[0058] With reference to FIG. 22, in another alternative embodiment
of the system shown in FIGS. 13-21, the solid actuator piston 1350
may be replaced with an auto-lashing actuator piston 1352. The
auto-lashing piston 1352 may include an actuator piston with a
hollow interior which receives an adjustable depth lash adjustment
screw-plunger 1353, spring 1355, and retaining collar 1357. The
adjustable depth lash adjustment screw-plunger may be partially
disposed in the hollow interior of the actuator piston 1352 and
extend out of the top of the actuator piston bore 1304. The
adjustable depth lash adjustment screw-plunger 1353 may have a
lower plunger end and the retaining collar 1357 may be disposed in
the hollow interior of the actuator piston 1352 above the lower
plunger end. The spring 1355 may be disposed between the retaining
collar 1357 and the lower plunger end. The auto-lashing actuator
piston 1352 may be maintained out of contact with sliding pin 1620
(as shown in FIG. 18) when the system is in an "actuator off"
position.
[0059] It will be apparent to those skilled in the art that
variations and modifications of the present invention can be made
without departing from the scope or spirit of the invention.
* * * * *