WO1997009517A1

WO1997009517A1 - Hydraulic valve assembly

Info

Publication number: WO1997009517A1
Application number: PCT/US1995/011141
Authority: WO
Inventors: Serge Vallve
Original assignee: Serge Vallve
Priority date: 1995-09-01
Filing date: 1995-09-01
Publication date: 1997-03-13
Also published as: AU3501795A

Abstract

A hydraulic valve member (10) substitutes for valve springs and provides static pressure to bias closed combustion-chamber valves. A valve (18) with the valve stem (16) is guided within a valve cylinder (12). The valve cylinder (12) has interior (20) and exterior (24) annular projections between which an annular hydraulic groove (30) is defined. The valve stem (16) is guided by the interior annular projection (20) and engages a valve piston (34) which reciprocates within the annular hydraulic groove (30). Hydraulic fluid present within the annular hydraulic groove (30) between the valve cylinder (12) and the valve piston (34) serves to urge the valve piston (34) toward the rocker arm (46) and away from the valve cylinder (12). Downward motion of the rocker arm (46) serves to open the valve (18); and upon release, the pressurized hydraulic fluid in the annular hydraulic groove (30) serves to close the valve (18).

Description

HYDRAULIC VALVE ASSEMBLY

TECHNICAL FIELD

The present invention relates to engine valves for internal-combustion engines and, more particularly, to valves operating at a static pressure, using a shared hydraulic system.

BACKGROUND ART In internal-combustion engines, whether diesel, gasoline, or otherwise powered, engine valves serve to ventilate the combustion chamber. Intake valves allow the flow of pre-mixed air and fuel into the combustion chamber. Exhaust valves allow the exit of the combustion products. Between the intake and exhaust of the air-fuel mixture and combustion products, the valves seal the combustion chamber so that the resulting explosion may drive the piston to turn the crankshaft. Operation of such valves is known in the art and generally well within the knowledge of the average professional automobile mechanic. In order the seat the valve against the side of the combustion chamber or cylinder, valve springs are used that bias the valve against the cylinder side. Such springs generally take an average of 80 to 140 pounds pressure per square inch (psi, 5.5E⁵ to 9.6E⁵ Pascal (Pa)) per valve spring in order to initially unseat the valve and open the cylinder to gas flow. At full compression, the pressure increases to 300 to 600 psi (2.0E⁶ to 4JE° Pa) per valve spring. This increased pressure is due to the well-known quality of springs to increase their opposing force with displacement.

Such pressure comes only from one source, namely, the running engine itself. As the engine must provide the energy to open and close its own valves, such energy cannot be used to propel the vehicle, diminishing fuel economy and engine 5 performance. It is more efficient and advantageous to have a valve biasing means which exerts a constant, not increasing, restoring force. Under such circumstances, the load upon the engine would be diminished and quicker and easier opening and closing of the valves would occur.

Some attempts have previously been made along these lines as reflected by the o following patents. Patent No. Inventor Issue Date

2,342,003 F.C. Meyer February 15, 1944

3,120,221 J. Lyons February 4, 1964

3,722,483 H. Overby March 27, 1973

4,484,545 J.G. Madsen November 27, 1984

4,592,313 F.H. Speckhart June 3, 1986

5,058,541 M. Shibata, et al. October 22, 1991

5, 190,262 D. Woollatt March 2, 1993

5,203,535 W.E. Richeson, et al. April 20, 1993

5,224,683 W.E. Richeson July 6, 1993

5,233,950 A. Umemoto, et al. August 10, 1993

5,287,829 N.E. Rose February 22, 1994

5,339,777 H.N. Cannon August 23, 1994

Some of the more pertinent patents shown above are described briefly below. M. Shibata. et al.. U.S. Pat. No. 5.058.541

This patent is directed to a valve operating system of an internal -combustion engine which includes provision for air pressure biasing the valve in a valve closing direction. Referring to Figure 1 , the assembly includes cam 8 mounted on cam shaft 7 for operation of valve 5. Numeral 8a denotes a circular base portion corresponding to a valve-closing timing of valve 5 while lobe portion 8b corresponds to a valve- opening timing of valve 5. The opening and closing of valve 5 is seen by noting valve opening 3. Piston 16 is fixed to valve shaft portion 5a and operates within sliding bore 10a in place of the usual valve spring closing mechanism. Air supply source 25 operates through check valve 23 and line 24 to pressurize chamber 13, thus biasing valve 5 in a closing direction.

F.H. Speckhart. U.S. Pat. No. 4.592.313

This reference describes a pneumatic valve return for an internal-combustion engine. The pneumatic valve return device is designed to replace mechanical springs in a cam operated valve mechanism. Figure 1 shows a valve 14 for operation within cylinder head 10 of an internal-combustion engine. Valve 14 may be either an intake or an exhaust valve for closing a port 17 in a combustion chamber 19. Valve stem 18 is supported for reciprocating within valve guide 24 and extends through cylinder head 10 between port 17 and actuating mechanism 22. The pneumatic valve return mechanism is denoted with numeral 12 and comprises a valve return cylinder 32 with bore 34 positioned on cylinder head 10 above valve 14. Valve return cylinder 32 would be approximately the same dimensions as a conventional valve spring. Piston 76 is fitted for sliding motion within cylinder bore 34 which is pressurized through conduit 98 for biasing the valve into a closed position when required.

A. Umemoto. et al.. U.S. Pat. No. 5.233.950

This patent is directed to a valve operating system for an internal-combustion multicylinder engine wherein the intake and exhaust valves are biased in their closed directions by air pressure instead of the usual valve springs. This reference is particularly interested in the pressure control valve and common relief passage and not the actual biasing of the engine valve in a closed direction as found in the previous two references discussed.

J.G. Madsen. U.S. Pat. No. 4.484.545

This reference is directed to a hydraulically actuated exhaust valve of an internal-combustion engine. The valve is biased for opening by the gas pressure found within the combustion chamber and is kept closed by an opposed hydraulic pressure. The device uses hydraulic fluid rather than the air as described in the previous patents discussed. The opening and closing movements of the exhaust valve is accomplished by means of the valve and duct arrangement shown in Figure 2 wherein reference numeral 19 indicates the high-pressure section which operates to bias the valve in a closing direction. This high-pressure system is connected to working chamber 18 (as seen in Figure 1) which is designated the "closing chamber" and which substitutes for the normal spring closing device found in conventional design valve systems. W.E. Richeson. et al.. U.S. Pat. No. 5.203.535

This patent is directed to a cam actuated valve assembly that includes a hydraulic spring device which provides the force to return the valve to the closed position. This system takes the place of the normal coil springs which are used in conventional valve assemblies.

J. Lvons. U.S. Pat. No. 3.120.221

This patent provides another example of a pneumatic valve return system in an internal-combustion engine. Referring to Figure 2, valve 24 is connected to valve cylinder 28 which is pressurized through inlet 54 from supply pipe 58 in order to bias valve 24 in a closing direction.

None of these previously mentioned attempts at achieving hydraulic engine valves advantageously provide the same features as those which are set forth herein. Additionally, the present system provides means by which present internal-combustion engines may be retrofitted in order to accommodate hydraulic valves. Despite the ease with which retrofitting is accomplished, the present invention operates in an efficient and reliable manner in order to provide engine valves that place a diminished load upon the engine while enhancing engine performance and maintaining proper gas flow to and from the cylinder.

DISCLOSURE OF INVENTION In order to reduce engine load and increase engine efficiency, engine-valve springs are replaced by coupled hydraulic means that bias and urge the engine valve to its seated position. A unique configuration of a piston-cylinder system is achieved, specifically adapted for use with internal-combustion engines.

A valve cylinder acts as a valve guide and is mounted to the engine head in lieu of the valve spring. The valve stem passes through the side of the cylinder. through the valve cylinder to engage the underside of the rocker arm. The portion of the valve cylinder adjacent the valve stem is cylindrically annular and defines a cylindrically annular groove between itself and the outer annular wall of the valve cylinder.

A cylindrically annular valve piston slideably fits and reciprocates within the annular groove of the valve cylinder. At the bottom of the valve cylinder, pressurized hydraulic fluid serves to push the valve piston upward. The upward motion of the

5 valve piston is stopped by a valve retainer that is coupled to the distal end of the valve stem. The upward biasing of the piston serves to urge the valve against the rocker arm.

O-rings present in both the valve piston and the valve cylinder serve to prevent the flow of hydraulic fluid out of the annular groove. A perforated dust cover o prevents particulate matter from descending into the hydraulic valve member. The perforations allow engine oil to lubricate the upper part of the hydraulic valve member. Hydraulic fluid, such as one (1) -weight sewing machine oil, serves to lubricate the lower part of the hydraulic valve member.

A series of valve cylinders are coupled by hydraulic lines in order to allow the s flow of hydraulic fluid throughout the assembly. A reservoir pressurized by a 12-volt

DC motor serves to apply constant pressure throughout the hydraulic valve assembly system. Note should be taken that the opening of one engine valve by one hydraulic valve member serves to exert pressure locally upon the assembly and hold closed (to a certain greater extent) other adjacent valves. o In an alternative embodiment, a controller may be coupled to a pressure sensor on the reservoir. The controller serves to prevent the engine from starting up and/or to shut off the engine should a catastrophic pressure loss occur. This prevents engine damage due to engine valves descending into the combustion chamber. A dashboard warning light coupled to the controller can serve to indicate low pressure within the 5 hydraulic reservoir. The controller may also monitor engine speed to limit or govern the maximum revolutions per minute (rpms) at which the engine runs.

BRIEF DESCRIPTION OF DRAWINGS

Figure 1 shows in cross section the hydraulic valve member of the present invention. o Figure 2 shows an isometric view of the present invention as it would be installed upon an eight-cylinder engine.

Figure 3 shows a plan view of the hydraulic reservoir and pump.

Figure 4 shows an alternative embodiment of the present system including the system controller allowing engine shut-off should pressure be lost.

BEST MODE FOR CARRYING OUT THE INVENTION

In order to provide constant seating bias to an engine valve, the present invention may be practiced as follows.

As shown in Figure 1, the hydraulic valve member 10 of the present invention serves to replace the valve springs currently in use on most engines. Such engines may be part of passenger vehicles, light and/or heavy trucks, off-road equipment, or other similar engines. The hydraulic valve member 10 engages the engine head 44 through the valve cylinder 12.

The valve cylinder 12 has a central projection 14 that protrudes into a recess present in the engine head 44. The central projection 14 serves as a foundation through which the valve cylinder, and therefore the hydraulic valve member 10, may be stably situated upon the engine head 44. An O-ring present in the central projection 14 provides a seal about the valve stem 16.

Valve cylinder 12 has two coaxial annular projections that extend away from the engine head 44 and toward rocker arm 46. The two projections are coaxial with the valve stem 16 of valve 18.

The first and interior annular projection 20 has a central passageway 22 that performs as a valve guide and through which valve stem 16 slideably slides and reciprocates. The interior annular projection 20 projects towards the rocker arm 46 approximately two thirds of the distance the second and exterior annular projection 24 does, allowing the piston (described in more detail below) to fit within the valve cylinder 12 despite its reciprocating action.

The exterior of the interior annular projection 20 is scored with two interior annular channels 26. These channels provide seats for O-rings that serve to seal the inner annular projection 20 with respect to the adjacent reciprocating valve piston 34. Atop the inner annular projection 20 is a piston bumper 28. Piston bumper 28 serves as a buffer or pad to prevent any metal -on-metal contact between the piston and the inner annular projection 20. Piston bumper 28 may be made of any resilient and sufficiently shock-absorbing material appropriate for the conditions within the hydraulic valve member 10. Such substances include high-grade plastics and the like. Spaced apart from the interior annular projection 20 is the exterior annular projection 24. The space between the two annular projections 20, 24 may be approximately a third of an inch (approximately eight millimeters). This gap defines the annular hydraulic groove 30 within which the valve piston 34 reciprocates and the hydraulic fluid is retained. The exterior annular projection 24 projects approximately one and three-quarter inches (approximately four and one-half centimeters) from the engine head 44.

The valve piston 34 fits about the valve retainer 32 to engage the valve stem 16. The valve piston 34 is generally cylindrically annular in shape with a series of three annular piston valve channels 36 etched about its exterior. O-rings, such as the type described in more detail below, fit within these annular grooves to provide a seal between the annular hydraulic groove 30 and the smooth interior side of the exterior projection of the hydraulic valve member 10.

A central aperture 38 is present in the valve piston 34 through which the valve stem 16 passes. In order to better engage the valve stem 16, the valve retainer 32 serves to intermediate the coupling between the valve piston 34 and the valve stem

16. The valve retainer 32 engages annular grooves etched into the distal end of the valve stem 16. The interior edge 40 of central aperture 38 is slightly chamfered in order to better engage the valve retainer 32.

The valve piston 34 enjoys a close but free fit within the annular hydraulic groove 30 defined between the interior annular projection 20 and the exterior annular projection 24. As indicated previously, O-rings are used to seal the hydraulic fluid within the annular hydraulic groove 30. Parker Seals manufactures high-quality O- rings and related devices and the use of Parker PARBAKS or an equivalent device in the present invention is contemplated. Parker PARBAKS prevent O-ring extrusion by better containing the O-ring within its channel. Furthermore, use of Parker

PARBAKS allows larger tolerances and machinability and provides excellent seals without deformation of the O-rings. Such O-rings 43, 45 are contemplated for use in the interior 26 and valve piston 36 channels and provide inner 43 and outer 45 sealing members, respectively.

In order to prevent particulate matter from falling into the working mechanism of the hydraulic valve member 10, a dust cover 42 attaches to the very distal end of the valve stem 16 and circumscribes the open rim of the exterior annular projection 24 to provide a cover over the valve piston 34, the annular hydraulic groove 30, the interior annual projection 20, and much of the valve stem 16. The dust cover 42 is perforated with small holes so that oil distributed about and within the valve cover 48 may fall and flow into the interior of the hydraulic valve member 10. The holes allow lubrication for the piston 34 as it slides within the valve cylinder 12.

As shown in Figure 2, the hydraulic valve members 10 of the present invention substitute for presently used valve springs. A hydraulic line 50 serves to supply the individual hydraulic valve members 10 of the hydraulic valve assembly 49 with pressurized hydraulic fluid. The hydraulic valve line 50 passes through the wall of the valve cover 48 to centrally distribute the pressurized hydraulic fluid. Similar hydraulic lines 52 serve to interconnect individual hydraulic valve assemblies with its adjacent neighbors. Terminal hydraulic valve members 54 use valve cylinders 12 having only one port, or aperture, 58 to the annular hydraulic groove 30. Non- terminal hydraulic valve members 56 use valve cylinders 12 having two oppositely opposed ports, or apertures, 58, 59 for the flow of hydraulic fluid therethrough. With this configuration, equal pressure is simultaneously distributed to all the valves of the system and is maintained by the hydraulic pressure system 60.

As shown in Figure 3, the hydraulic pressure system 60 uses a hydraulic fluid reservoir 62 coupled to a 12-volt DC motor 64 that drives a pressurizing pump 66.

The motor 64 is coupled to a pressure switch, or sensor. 68 that controls the operation of the motor 64 to maintain hydraulic fluid pressure. When the pressure sensor 68 detects a lowering of the hydraulic fluid pressure, it engages the motor 64 to increase the pressure. Likewise, should the pressure in the hydraulic reservoir 62 be sufficient, the pressure sensor 68 disengages the pressure motor 64. One pressure at which the hydraulic pressure system 60 may maintain the hydraulic fluid is 110 psi (7.5E⁵ Pa). One (1) -weight sewing machine oil is contemplated as providing one type of hydraulic fluid 70 for the present invention. Other hydraulic fluids may also be advantageously used in the present system, including pressurized gas which may be saturated with oil mist in order to provide lubrication for the piston 34. The sealing means set forth in the present description is seen as providing adequate closure so that the gas does not escape from the annular hydraulic groove 30.

As shown in Figure 4, the hydraulic pressure system 60 may be coupled to a controller 80 in order to prevent engine damage should hydraulic pressure drop severely or be lost entirely. The controller 80 is coupled to the pressure switch 68 as well as switched 82 and direct 84 supplies of 12-volt DC power. The controller 80 may also be coupled to the #1 spark plug 86 to provide a means by which engine rpm^'s may be detected. The controller 80 is coupled to the ignition switch 88 and serves to prevent the engine from starting until sufficient pressure has been adequately achieved in the hydraulic pressure system 60. Once adequate hydraulic pressure has been achieved via the motor-driven pump 66, an in-dash lamp or other indicator 90 may be used to signal the driver that the engine is ready to be started. Likewise, a similar dashboard indicator can be used to indicate any significant loss in hydraulic pressure. If the hydraulic pressure is inadequate to operate the hydraulic valve assembly, the controller 80 may shut off the engine. Catastrophic loss of hydraulic pressure would then not result in extensive engine damage.

By monitoring the engine's speed (rpms), the controller 80 may also limit or govern peak engine rpms. Should engine rpms exceed a pre-set limit (such as 7000 rpms), ignition spark may be withheld from the spark plugs to reduce engine rpms. Once the engine speed has fallen below the pre-set limit, engine spark may be returned to the spark plugs, maintaining the running of the engine.

When the hydraulic pressure system 60 pressurizes the hydraulic fluid 70, the pressure is distributed throughout the hydraulic valve members 10 through the hydraulic lines 50, 52. Once pressurized, the hydraulic fluid 70 urges the valve pistons 34 toward the rocker arm 46 and against the valve retainers 32 at the pressure of the hydraulic fluid 70. The upward bias of the valve pistons 34 and valve stems 16 serve to seat the valves 18 against the interior of the combustion chambers. When rocker arm 46 descends as from motivation by a push rod, the pressure of the hydraulic fluid 70 is overcome and the valve piston 34 and the valve stem 16 descend, depressing the valve piston 34 within the annular hydraulic groove 30, and opening the valve 18. The descent of the valve piston 34 serves to locally exert increased pressure upon the hydraulic fluid 70, increasing the upward biasing of neighboring valve pistons 34 due to the hydraulic fluid 70. As the push rod descends to release the rocker arm 46, the pressure maintained by the hydraulic fluid 70 serves to urge the piston 34 upward, likewise urging upward the valve stem 16 so that the valve 18 may be seated against the combustion chamber interior. Preliminary tests were held, indicating that, by reducing the resistance on the engine, the hydraulic valve members of the present invention may significantly increase engine output and the revolutions per minute (φm) of the engine. In one such preliminary test, a 1965 Ford Mustang with a 289-cubic-inch V8 engine saw an increase of horsepower from 180 horsepower to approximately 500 horsepower (1.34E⁵ watts to 3.73E⁵ watts). Installation of the present invention allowed the engine to operate well at approximately 8500 rpm when the previous maximum engine speed was approximately 5000 φm..

The present system is seen as being advantageously used in both gasoline- and diesel-powered engines. Engines using other types of fuel may otherwise advantageously use the present invention as well, such fuels including: propane, methanol, alcohol, natural gas, and the like. While certain dimensions have been given explicitly in the description above, it should be noted that such dimensions are given for relative measurement puφoses only and do not limit the size of the hydraulic valve member set forth herein. Variations on the present invention may be achieved by those knowledgeable regarding aspects of the present invention without departing from the scope of the claims herein.

INDUSTRIAL APPLICABILITY

The present invention may be applied industrially in conjunction with most internal-combustion engines. Where valve springs are used to seat combustion chamber valves, the present hydraulic valve member may be substituted therefore.

Claims

CLAIMSWhat is claimed is:

1. A hydraulic valve member (10) for an internal-combustion engine, 2 comprising: a valve cylinder (12), said valve cylinder defining a hydraulic ₄ groove (30) for retaining hydraulic fluid; a valve piston (34), said valve piston closely and sealingly 6 reciprocating within said hydraulic groove (30), said valve piston (34) sealing said hydraulic groove (30) and preventing hydraulic fluid flow g therefrom past a portion of said valve piston (34) within said hydraulic groove (30); whereby io pressurized hydraulic fluid present in said hydraulic groove (30) urges said valve piston (34) away from said valve cylinder (12) to bias i2 closed a valve (18) coupled to said valve piston (34).

2. The hydraulic valve member (10) for an internal-combustion engine as 2 set forth in Claim 1 , wherein said valve cylinder defines (12) at least one hydraulic fluid aperture (58) communicating with said hydraulic groove (30), ₄ said hydraulic fluid aperture (58) allowing hydraulic fluid flow therethrough to and from said hydraulic groove.

3. The hydraulic valve member (10) for an internal-combustion engine as 2 set forth in Claim 2, wherein said valve cylinder (12) defines a second hydraulic fluid aperture (59) communicating with said hydraulic groove (30), A said second hydraulic fluid aperture allowing hydraulic fluid flow therethrough.

4. The hydraulic valve member (10) for an internal-combustion engine as 2 set forth in Claim 1 . wherein said valve cylinder ( 12) further comprises an interior projection (20), said interior projection (20) forming an inner wall of said hydraulic groove (30).

5. The hydraulic valve member (10) for an internal-combustion engine as set forth in Claim 4, wherein said interior projection (20) defines a central passageway (22) slideably accommodating a valve stem (16), said interior projection (20) guiding said valve stem (16) as said valve stem (16) reciprocates within said central passageway (22).

6. The hydraulic valve member (10) for an internal-combustion engine as set forth in Claim 5, wherein said interior projection (20) defines at least one interior annular channel (26), said at least on interior annular channel (26) adjacent said valve piston (34) and circumscribing said interior projection (20).

7. The hydraulic valve member (10) for an internal-combustion engine as set forth in Claim 6, wherein said interior projection (20) defines a second interior annular channel (26), said second interior annular channel (26), adjacent said valve piston (34) and circumscribing said interior projection (20).

8. The hydraulic valve member (10) for an internal-combustion engine as set forth in Claim 6, wherein an inner sealing member (43) is seated in said at least one interior annular channel between said interior projection (20) and said valve piston (34), said inner sealing member (43) establishing and maintaining a seal between said interior projection (20) and said valve piston (34).

9. The hydraulic valve member (10) for an internal-combustion engine as set forth in Claim 4, wherein said valve cylinder (12) further comprises an exterior projection (24), said exterior projection (24) forming an outer wall of said hydraulic groove (30).

10. The hydraulic valve member (10) for an internal-combustion engine as set forth in Claim 9, wherein said exterior projection (24) is longer than said interior projection (20).

11. The hydraulic valve member (10) for an internal-combustion engine as set forth in Claim 10, wherein an inner surface of said exterior projection (24) forms said outer wall of said hydraulic groove (30) and is smooth.

12. The hydraulic valve member (10) for an internal-combustion engine as set forth in Claim 9. wherein said valve piston (34) closely and sealingly reciprocates in said hydraulic groove (30) between said interior (20) and exterior (24) projections of said valve cylinder (12).

13. The hydraulic valve member (10) for an internal-combustion engine as set forth in Claim 12, wherein said valve piston (34) defines a central aperture (38) fitting about said valve stem (16), said valve piston (34) coupled to downward motion of said valve stem (16) and said valve stem (16) coupled to upward motion of said valve piston (34).

14. The hydraulic valve member (10) for an internal-combustion engine as set forth in Claim 13, wherein said valve piston (34) defines at least one annular valve piston channel (36), said annular valve piston channel (36) adjacent said exterior projection (24) and circumscribing said valve piston (34).

15. The hydraulic valve member (10) for an internal-combustion engine as set forth in Claim 14. wherein said valve piston (34) defines a second annular valve piston channel (36), said second annular valve piston channel (36) adjacent said exterior projection (24) and circumscribing said valve piston (34).

16. The hydraulic valve member (10) for an internal-combustion engine as set forth in Claim 14, wherein an outer sealing member (45) is seated in said at least one annular valve piston channel (36) between said valve piston (34) Λ and said exterior projection (24), said sealing member (45) establishing and maintaining a seal between said valve piston (34) and said exterior projection (24).

17. A hydraulic valve member (10) for an internal-combustion engine,

2 comprising: a valve cylinder (12); and ₄ a valve piston (34); said valve cylinder (12) defining a hydraulic groove (30) for 6 retaining hydraulic fluid, said valve cylinder (12) defining at least one hydraulic fluid aperture (58) communicating with said hydraulic groove 8 (30), said at least one hydraulic fluid aperture (58) allowing hydraulic fluid flow therethrough to and from said hydraulic groove (30), said io valve cylinder (12) comprising: an interior projection (20), said interior projection (20) i2 forming an inner wall of said hydraulic groove (30), said interior projection (20) defining a central passageway (22) slideably i4 accommodating a valve stem (16), said interior projection (20) guiding said valve stem (16) as said valve stem (16) reciprocates i6 within said central passageway (22), said interior projection (20) defining at least one interior annular channel (26), said at least one ie interior annular channel (26) adjacent said valve piston (34) and circumscribing said interior projection (20), wherein an inner sealing 20 member (43) is seated in said at least one interior annular channel

(26) between said interior projection (20) and said valve piston (34), 22 said inner sealing member (43) establishing and maintaining a seal between said interior projection (20) and said valve piston (34): and 24 an exterior projection (24), said exterior projection (24) forming an outer wall of said hydraulic groove (30), said exterior 26 projection (24) being longer than said interior projection (20), an inner surface of said exterior projection (24) forming said outer wall 8 of said hydraulic groove (30) and being smooth; said valve piston (34) closely and sealingly reciprocating within 0 said hydraulic groove (30) between said interior (20) and exterior (24) projections of said valve cylinder (34), said valve piston (34) sealing 2 said hydraulic groove (30) and preventing hydraulic fluid flow therefrom past a poπion of said valve piston (34) within said hydraulic groove (30), said valve piston (34) defining a central valve stem apeπure (38) fitting about said valve stem (16), said valve piston (34) 6 coupled to downward motion of valve stem (16) and said valve stem

(16) coupled to upward motion of said valve piston (34), said valve 8 piston (34) defining at least one annular valve piston channel (36), said annular valve piston channel (36) adjacent said inner surface of said 0 exterior projection (24) and circumscribing said valve piston (34), wherein an outer sealing member (45) is seated in said at least one 2 annular valve piston channel (36) between said valve piston (34) and said exterior projection (24), said outer sealing member (45) 4 establishing and maintaining a seal between said valve piston (34) and said exterior projection (24); whereby 6 pressurized hydraulic fluid present in said hydraulic groove (30) urges said valve piston (34) away from said valve cylinder (12) to bias 8 a valve (18) coupled to said valve piston (34).

18. A hydraulic valve assembly system for an internal-combustion engine,

2 comprising: a hydraulic valve member (49) having individual hydraulic valve ₄ members (10) hydraulically biasing closed valves (18) of an engine head (44); e a reservoir (62) of pressurized hydraulic fluid coupled to said hydraulic valve member (48) by hydraulic fluid lines (50), said s reservoir (62) having a hydraulic fluid pressure sensor (68) indicating pressure present in said reservoir; and 10 a controller (80), said controller coupled to said hydraulic fluid pressure sensor (68) and coupled to an ignition switch (88), said i2 controller (80) sensing a signal from said hydraulic fluid pressure sensor (68) and disabling ignition if said hydraulic fluid pressure sensor ι₄ (68) indicates inadequate hydraulic fluid pressure to operate said hydraulic valve member (48); whereby i6 damage to the internal combustion engine is minimized should inadequate hydraulic fluid pressure occur.

19. The hydraulic valve member system for an internal-combustion engine 2 as set forth in Claim 18, wherein said controller (80) additionally shuts down an engine associated with said hydraulic valve member (48) should said ₄ hydraulic fluid pressure sensor (68) indicate inadequate hydraulic fluid pressure to operate said hydraulic valve member (49).

20. The hydraulic valve member system for an internal-combustion engine as set forth in Claim 18, wherein said controller (80) additionally withholds engine spark of an engine associated with said hydraulic valve member (48) ₄ should speed of said engine exceed a certain pre-set limit.