US20050000476A1 - System and method for improving performance of hydraulic actuating system - Google Patents
System and method for improving performance of hydraulic actuating system Download PDFInfo
- Publication number
- US20050000476A1 US20050000476A1 US10/839,143 US83914304A US2005000476A1 US 20050000476 A1 US20050000476 A1 US 20050000476A1 US 83914304 A US83914304 A US 83914304A US 2005000476 A1 US2005000476 A1 US 2005000476A1
- Authority
- US
- United States
- Prior art keywords
- lost motion
- reservoir
- hydraulic fluid
- hydraulic
- engine
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
- F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
- F01L9/11—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/20—Adjusting or compensating clearance
- F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
- F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
- F15B7/001—With multiple inputs, e.g. for dual control
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
- F15B7/003—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors with multiple outputs
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
- F15B7/005—With rotary or crank input
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
- F15B7/06—Details
- F15B7/10—Compensation of the liquid content in a system
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/08—Shape of cams
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
- F01L2001/34423—Details relating to the hydraulic feeding circuit
- F01L2001/34426—Oil control valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
- F01L2001/34423—Details relating to the hydraulic feeding circuit
- F01L2001/34446—Fluid accumulators for the feeding circuit
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L2305/00—Valve arrangements comprising rollers
Definitions
- the present invention relates to systems and methods of improving the performance of a hydraulic system.
- the present invention relates to a reservoir system and method using same that provides hydraulic fluid to a lost motion system disposed in an internal combustion engine and used to actuate engine valves.
- Valve actuation in an internal combustion engine is required in order for the engine to produce positive power, as well as to produce engine braking.
- intake valves may be opened to admit fuel and air into a cylinder for combustion.
- the exhaust valves may be opened to allow combustion gas to escape from the cylinder.
- the exhaust valves may be selectively opened to convert, at least temporarily, an internal combustion engine of compression-ignition type into an air compressor.
- This air compressor effect may be accomplished by cracking open one or more exhaust valves near piston top dead center position for compression-release type braking, or by maintaining one or more exhaust valves in a cracked open position for much or all of the piston motion for bleeder type braking.
- the engine develops retarding horsepower to help slow the vehicle down. This can provide the operator increased control over the vehicle and substantially reduce wear on the service brakes of the vehicle.
- a properly designed and adjusted engine brake can develop retarding horsepower that is a substantial portion of the operating horsepower developed by the engine in positive power.
- the engine cylinder intake and exhaust valves may be opened and closed by fixed profile cams in the engine, and more specifically by one or more fixed lobes which may be an integral part of each of the cams.
- the use of fixed profile cams can make it difficult to adjust the timings and/or amounts of engine valve lift needed to optimize valve opening times and lift for various engine operating conditions, such as different engine speeds.
- the lost motion system 100 may include a master piston 110 hydraulically linked to a slave piston 120 by the hydraulic passage 130 .
- a check valve 140 allows hydraulic fluid to be supplied to and retained in the hydraulic passage 130 .
- a control valve 150 permits fluid in the hydraulic passage 130 to be selectively released.
- a cam 200 may provide the “maximum” (longest dwell and greatest lift) motion needed for engine operating conditions.
- the lost motion system 100 may be included in the valve train linkage, intermediate of the valve 300 to be opened and the cam 200 providing the maximum motion.
- Cam motion imparted to the master piston 110 may be transferred to the slave piston 120 , and thus the engine valve 300 , when the hydraulic passage 130 is full of fluid.
- the engine valve 300 e.g., exhaust or intake valve
- the control valve 150 allows the lost motion system to subtract or lose part or all of the motion imparted by the cam to the master piston 110 by releasing fluid from the hydraulic passage 130 .
- Lost motion systems while beneficial in many aspects, have also been subject to some drawbacks.
- the use of hydraulics may result in initial starting difficulties as the result of a lack of hydraulic fluid in the system.
- fluid in the hydraulic passage 130 may drain out of the system due to leakage past the master piston 110 , the slave piston 120 , the check valve 140 , and/or the control valve 150 .
- the oil supply pump (not shown) that provides hydraulic fluid to the passage 130 may not be capable of supplying fluid quickly enough.
- it is possible that the hydraulic passage 130 may not be completely filled until more than a minute after initial cranking of the engine.
- Operation of the lost motion system 100 may also be interfered with by the presence of air in the hydraulic passage 130 connecting the master and slave pistons.
- Air is not a hydraulic fluid, but rather a compressible fluid. Air entrained in the hydraulic passage 130 can cause the hydraulic circuit to compress instead of transferring motion from the master piston 110 to the slave piston 120 . This can result in loss of the cam motion even when it is desired that it not be lost.
- the system comprises: a reservoir; a gallery circuit connected to the reservoir, wherein the gallery circuit is adapted to be connected to one or more lost motion systems; and a control valve adapted to provide selective hydraulic communication between the gallery circuit and the one or more lost motion systems.
- Applicant has further developed an innovative method of providing hydraulic fluid to a lost motion system during start up of an internal combustion engine.
- the method comprises the steps of: providing hydraulic fluid in a reservoir, the reservoir being disposed relative to the lost motion system to facilitate the flow of hydraulic fluid to the lost motion system under the influence of gravity; blocking hydraulic communication between the reservoir and the lost motion system during application of at least an initial portion of an engine valve event motion to the lost motion system; and providing hydraulic communication between the reservoir and the lost motion system during application of at least a later portion of the engine valve event motion to the lost motion system.
- FIG. 1 is a cross-section of a lost motion valve actuation system.
- FIG. 2 is a cross-section of a lost motion valve actuation system including a system for charging the lost motion valve actuation system with hydraulic fluid in accordance with a first embodiment of the present invention.
- FIG. 3 is a cross-section of a lost motion valve actuation system including a system for charging the lost motion valve actuation system with hydraulic fluid in accordance with an alternative embodiment of the present invention.
- FIG. 4 is a cross-section of a portion of a lost motion valve actuation system including an orthogonal master-slave piston arrangement in accordance with an alternative embodiment of the present invention.
- FIG. 5 is a graph of crank angle position versus cam lobe motion and control valve position which illustrates an example of control valve timing that may be employed in a method embodiment of the present invention.
- FIG. 6 is a cross-section of a lost motion valve actuation system including a system for charging the lost motion valve actuation system with hydraulic fluid in accordance with an alternative embodiment of the present invention.
- FIG. 7 is a cross-section of a lost motion valve actuation system including a system for charging the lost motion valve actuation system with hydraulic fluid in accordance with an alternative embodiment of the present invention.
- each lost motion system 100 may be disposed between a cam 200 and an engine valve 300 .
- the cams 200 may include one or more cam lobes 210 , 220 , etc., for imparting an engine valve actuation motion to the lost motion system 100 .
- the lost motion system 100 is shown to act on a single engine valve 300 , however, it is appreciated that the lost motion system 100 may act on more than one engine valve through a valve bridge in alternative embodiments.
- each lost motion system 100 may include a master piston 110 hydraulically linked to a slave piston 120 by a hydraulic passage 130 .
- a control valve 150 is disposed in the hydraulic passage 130 so that it may selectively block or unblock the hydraulic passage. Electronic or mechanical control of the control valve 150 permits fluid to enter the hydraulic passage 130 when the control valve 150 is in an open position (as shown). When the control valve 150 is closed (downward as shown in FIG. 2 ), hydraulic fluid is trapped in the passage 130 , thereby hydraulically locking the master piston 110 to the slave piston 120 . Reopening the control valve 150 may also allow fluid in the passage 130 to be selectively released, thereby unlocking the master piston 110 from the slave piston 120 .
- An optional accumulator piston 160 may assist in maintaining low pressure fluid in the vicinity of the hydraulic passage 130 so that it may be drained and refilled rapidly.
- the optional accumulator piston 160 may be particularly useful when the lost motion system 100 is used to provide variable valve actuation.
- the control valve 150 may be a high-speed trigger valve. High-speed trigger valves may be capable of being opened and closed one or more times per engine cycle to enable locking and unlocking the master piston 110 from the slave piston 120 one or more times per engine cycle.
- Hydraulic fluid may be supplied to the hydraulic passage 130 by the reservoir system 400 .
- the reservoir system 400 may include a reservoir 410 , a low pressure feed 420 , an optional check valve 430 , an inlet port 440 , an air bleed opening 450 , and a common gallery circuit 460 .
- Hydraulic fluid such as, for example, engine oil, may be provided from the low pressure feed 420 to the reservoir 410 .
- the optional check valve 430 may prevent hydraulic fluid in the reservoir 410 from flowing back to the low pressure feed 420 .
- the reservoir system 400 may include an air bleed opening 450 near the top of the reservoir 410 .
- the air bleed 450 may allow air entrained in the hydraulic fluid that enters the reservoir 410 from the low pressure feed 420 to exit the system before it enters the one or more lost motion systems 100 .
- the air bleed opening 450 may be sized to allow small quantities of air to exit from the reservoir system 400 freely, while still offering restriction to the exit of hydraulic fluid, even at relatively high pressure.
- the air bleed 450 may also allow air to enter the reservoir 410 to make up for hydraulic fluid that is fed by the reservoir to the gallery circuit 460 . This may prevent a vacuum effect from preventing hydraulic fluid from flowing out of the reservoir 410 under a relatively small gravitational force.
- the air bleed 450 may permit air that does become entrained in the hydraulic fluid of the lost motion systems 100 to bubble up and out of these systems over time.
- the inlet port 440 may be located near the top of the reservoir 410 . Placement of the inlet port 440 near the top of the reservoir 410 may enhance the ability of the reservoir system 400 to allow air entrained in the fluid provided by the low pressure feed 420 to exit through the air bleed 450 .
- the gallery circuit 460 may provide hydraulic fluid from the reservoir system 400 to each of the possible plurality of lost motion systems 100 .
- the reservoir system 400 may be located at any point along the expanse of the gallery circuit 460 .
- the upper level of hydraulic fluid in the reservoir 410 may be above the level of the hydraulic passages 130 so that gravity can facilitate the flow of hydraulic fluid from the reservoir to the hydraulic passages.
- each lost motion system 100 may benefit from incorporating a reservoir system 400 local to the lost motion system. These local reservoir systems 400 may be integrally incorporated into the housing of each lost motion system 100 .
- the low pressure feed 420 need not connect directly to the reservoir 410 .
- the low pressure feed 420 may connect to the gallery circuit 460 directly, instead of connecting through the reservoir 410 .
- the lost motion system 100 may further comprise an optional passage 170 for bypassing the control valve 150 , and an optional check valve 175 disposed in the passage 170 .
- the optional passage 170 and check valve 175 may permit hydraulic fluid to enter and refill the hydraulic passage 130 when there is insufficient time to open the control valve 150 between engine valve events, for example, in a variable valve actuation system.
- operation of the lost motion system 100 may begin by filling the reservoir 410 with hydraulic fluid from the low pressure feed 420 .
- the optional check valve 430 permits hydraulic fluid flow into the reservoir 410 from the low pressure feed 420 , but does not permit a substantial amount of fluid to flow back to the low pressure feed from the reservoir.
- control valve 150 may be normally open, or normally closed.
- a normally open control valve 150 As shown in FIG. 2 , an embodiment of the present invention including a normally open control valve 150 will be described. Embodiments of the present invention may use either a normally open or a normally closed control valve 150 .
- the reservoir 410 may contain a substantial amount of hydraulic fluid.
- each of the control valves 150 open, thereby connecting the hydraulic passage 130 from the gallery circuit 460 and the reservoir 410 , as shown in FIG. 2 .
- hydraulic fluid may leak out of the hydraulic passage 130 due to leakage past the master piston 110 and the slave piston 120 . Hydraulic leakage may also occur past the accumulator 160 .
- the accumulator 160 may be disposed so that it is inverted as compared to its position shown in FIG. 2 . The accumulator 160 position in FIG.
- the master piston 110 and/or the slave piston 120 may be inverted to limit the drainage of hydraulic fluid.
- the reservoir 410 may be provided with a sufficiently great amount of hydraulic fluid that it will continue to retain a useful amount of fluid over a prolonged period even if a low to moderate level of fluid leakage occurs past the accumulator 160 .
- the bottom of the reservoir 410 may be positioned below the level of the gallery circuit 460 such that the fluid in the reservoir 410 is prevented from being entirely drained out.
- the reservoir feed 440 may be positioned at the top of the reservoir 410 to prevent hydraulic fluid drainage into the engine should the check valve 430 fail or be absent.
- the hydraulic passage 130 may be so depleted of hydraulic fluid that displacement of the master piston 110 fails to result in sufficient displacement of the slave piston 120 to produce a desired actuation of engine valve 300 .
- Hydraulic fluid may be supplied by the reservoir 410 to the hydraulic passage 130 at this time.
- the supply of fluid to the hydraulic passage 130 may begin by opening the control valve 150 .
- opening the control valve 150 fluid is permitted to flow from the reservoir 410 , through the gallery circuit 460 to the hydraulic passage 130 .
- the gallery circuit 460 may be located relative to the individual lost motion systems 100 so that gravity encourages the flow of fluid from the gallery circuit to the individual lost motion systems.
- the flow of fluid into each of the hydraulic passages 130 may be further encouraged by the pumping action of the master piston 110 in conjunction with selective control of the control valve 150 .
- the control valve 150 may be open so that fluid may be drawn into the hydraulic passage 130 by the vacuum created by the master piston.
- the control valve 150 may be maintained closed so that the master piston 110 does not drive fluid back out of the hydraulic passage 130 . This cycle may be repeated until the passage 130 and accumulator 160 are refilled with fluid.
- the high pressure generated in the master-slave circuit may force any air in the circuit out past the close clearance between the master piston 110 and the slave piston 120 and their respective bores.
- the master piston 110 may be disposed in a direction substantially orthogonal or perpendicular to the orientation of the slave piston 120 , such that any air in the circuit may be located at the piston/bore interface and may be readily forced out.
- FIG. 5 An example of the control valve timing that may be used to further enhance the refilling of the lost motion system 100 is provided in FIG. 5 .
- the cam may be provided with one or more cam lobes that provide a main exhaust motion 500 and a compression release motion 510 , for example.
- the control valve position may be maintained in an open position until just prior to the main exhaust motion 500 . At this time the control valve may be closed, and maintained closed until approximately the mid-point of the main exhaust motion 500 , at which time the control valve may be re-opened.
- This timing may be used during the first part of cranking (engine start-up) to facilitate refilling of the circuits, after which time the normal starting valve motion may be generated. It is contemplated that the control valve timing of embodiments of the present invention may be used in conjunction with other engine valve events, such as, a main intake valve event and an engine braking valve event.
- the one or more lost motion systems 100 may include a collapsible tappet assembly 180 operatively connected to a rocker arm 182 , which, in turn, is operatively connected to one or more engine valves 300 .
- Other embodiments of the one or more lost motion systems 100 for selectively losing part or all of the motion imparted to the system 100 are considered well within the scope and spirit of the present invention.
Abstract
A system and method is disclosed for supplying hydraulic fluid to a lost motion system in an internal combustion engine. The system may comprise a reservoir; a gallery circuit connected to the reservoir, wherein the gallery circuit is adapted to be connected to the one or more lost motion systems; and a control valve adapted to provide selective hydraulic communication between the gallery circuit and the one or more lost motion systems.
Description
- This application relates to and claims priority on U.S. Provisional Application No. 60/468,088, filed May 6, 2003 and entitled “Hydraulic Circuit to Improve Starting of Hydraulic Actuating System,” a copy of which is incorporated herein by reference.
- The present invention relates to systems and methods of improving the performance of a hydraulic system. In particular, the present invention relates to a reservoir system and method using same that provides hydraulic fluid to a lost motion system disposed in an internal combustion engine and used to actuate engine valves.
- Valve actuation in an internal combustion engine is required in order for the engine to produce positive power, as well as to produce engine braking. During positive power, intake valves may be opened to admit fuel and air into a cylinder for combustion. The exhaust valves may be opened to allow combustion gas to escape from the cylinder.
- During engine braking, the exhaust valves may be selectively opened to convert, at least temporarily, an internal combustion engine of compression-ignition type into an air compressor. This air compressor effect may be accomplished by cracking open one or more exhaust valves near piston top dead center position for compression-release type braking, or by maintaining one or more exhaust valves in a cracked open position for much or all of the piston motion for bleeder type braking. In doing so, the engine develops retarding horsepower to help slow the vehicle down. This can provide the operator increased control over the vehicle and substantially reduce wear on the service brakes of the vehicle. A properly designed and adjusted engine brake can develop retarding horsepower that is a substantial portion of the operating horsepower developed by the engine in positive power.
- For both positive power and engine braking applications, the engine cylinder intake and exhaust valves may be opened and closed by fixed profile cams in the engine, and more specifically by one or more fixed lobes which may be an integral part of each of the cams. The use of fixed profile cams can make it difficult to adjust the timings and/or amounts of engine valve lift needed to optimize valve opening times and lift for various engine operating conditions, such as different engine speeds.
- One method of adjusting valve timing and lift, given a fixed cam profile, has been to incorporate a “lost motion” device in the valve train linkage between the valve and the cam. Lost motion is the term applied to a class of technical solutions for modifying the valve motion proscribed by a cam profile with a variable length mechanical, hydraulic, or other linkage means. An example of a lost
motion system 100 is shown inFIG. 1 . The lostmotion system 100 may include amaster piston 110 hydraulically linked to aslave piston 120 by thehydraulic passage 130. Acheck valve 140 allows hydraulic fluid to be supplied to and retained in thehydraulic passage 130. Acontrol valve 150 permits fluid in thehydraulic passage 130 to be selectively released. In connection with the lostmotion system 100, acam 200 may provide the “maximum” (longest dwell and greatest lift) motion needed for engine operating conditions. - The lost
motion system 100 may be included in the valve train linkage, intermediate of thevalve 300 to be opened and thecam 200 providing the maximum motion. Cam motion imparted to themaster piston 110 may be transferred to theslave piston 120, and thus theengine valve 300, when thehydraulic passage 130 is full of fluid. In this manner, the engine valve 300 (e.g., exhaust or intake valve), may be actuated by the lost motion system only when hydraulic fluid is maintained in thehydraulic passage 130. Selective operation of thecontrol valve 150 allows the lost motion system to subtract or lose part or all of the motion imparted by the cam to themaster piston 110 by releasing fluid from thehydraulic passage 130. - Other examples of such systems are provided in U.S. patent application serial number Vorih et al., U.S. Pat. No. 5,829,397 (Nov. 3, 1998), Hu, U.S. Pat. No. 6,125,828 (Oct. 3, 2000), and Hu, U.S. Pat. No. 5,680,841 (Oct. 28, 1997), which are assigned to the same assignee as the present application, and which are incorporated herein by reference.
- Lost motion systems, while beneficial in many aspects, have also been subject to some drawbacks. The use of hydraulics may result in initial starting difficulties as the result of a lack of hydraulic fluid in the system. With respect to the lost
motion system 100 shown inFIG. 1 , for example, when the engine in which it is installed is shut off for a period of time, fluid in thehydraulic passage 130 may drain out of the system due to leakage past themaster piston 110, theslave piston 120, thecheck valve 140, and/or thecontrol valve 150. As a result, when the engine is started there may be no fluid in thehydraulic passage 130 to enable motion from thecam 200 to be transferred to theengine valve 300. The oil supply pump (not shown) that provides hydraulic fluid to thepassage 130 may not be capable of supplying fluid quickly enough. In some instances, it is possible that thehydraulic passage 130 may not be completely filled until more than a minute after initial cranking of the engine. In a multi-cylinder engine, there may be numerous lostmotion systems 100 that must be charged with hydraulic fluid. - If actuation of the
engine valve 300 is required immediately during engine starting, as is often the case with variable valve actuation (WA) systems, this lack of hydraulic fluid can frustrate and prevent starting, or cause engine damage. It may be particularly difficult to charge thesystem 100 with hydraulic fluid when the fluid is cold and has a lower viscosity. - It is therefore an advantage of some, but not necessarily all, embodiments of the present invention to improve upon charging a lost motion valve actuation system with hydraulic fluid.
- Operation of the lost
motion system 100 may also be interfered with by the presence of air in thehydraulic passage 130 connecting the master and slave pistons. Air is not a hydraulic fluid, but rather a compressible fluid. Air entrained in thehydraulic passage 130 can cause the hydraulic circuit to compress instead of transferring motion from themaster piston 110 to theslave piston 120. This can result in loss of the cam motion even when it is desired that it not be lost. - It is therefore an advantage of some, but not necessarily all, embodiments of the present invention to improve upon the venting of air from the hydraulic circuit connecting the master piston to the slave piston in a lost motion system.
- Additional advantages of various embodiments of the invention are set forth, in part, in the description that follows and, in part, will be apparent to one of ordinary skill in the art from the description and/or from the practice of the invention.
- Responsive to the foregoing challenges, Applicant has developed an innovative reservoir system for supplying hydraulic fluid to a lost motion system in an internal combustion engine. In one embodiment, the system comprises: a reservoir; a gallery circuit connected to the reservoir, wherein the gallery circuit is adapted to be connected to one or more lost motion systems; and a control valve adapted to provide selective hydraulic communication between the gallery circuit and the one or more lost motion systems.
- Applicant has further developed an innovative method of providing hydraulic fluid to a lost motion system during start up of an internal combustion engine. In one embodiment, the method comprises the steps of: providing hydraulic fluid in a reservoir, the reservoir being disposed relative to the lost motion system to facilitate the flow of hydraulic fluid to the lost motion system under the influence of gravity; blocking hydraulic communication between the reservoir and the lost motion system during application of at least an initial portion of an engine valve event motion to the lost motion system; and providing hydraulic communication between the reservoir and the lost motion system during application of at least a later portion of the engine valve event motion to the lost motion system.
- 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.
- 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.
-
FIG. 1 is a cross-section of a lost motion valve actuation system. -
FIG. 2 is a cross-section of a lost motion valve actuation system including a system for charging the lost motion valve actuation system with hydraulic fluid in accordance with a first embodiment of the present invention. -
FIG. 3 is a cross-section of a lost motion valve actuation system including a system for charging the lost motion valve actuation system with hydraulic fluid in accordance with an alternative embodiment of the present invention. -
FIG. 4 is a cross-section of a portion of a lost motion valve actuation system including an orthogonal master-slave piston arrangement in accordance with an alternative embodiment of the present invention. -
FIG. 5 is a graph of crank angle position versus cam lobe motion and control valve position which illustrates an example of control valve timing that may be employed in a method embodiment of the present invention. -
FIG. 6 is a cross-section of a lost motion valve actuation system including a system for charging the lost motion valve actuation system with hydraulic fluid in accordance with an alternative embodiment of the present invention. -
FIG. 7 is a cross-section of a lost motion valve actuation system including a system for charging the lost motion valve actuation system with hydraulic fluid in accordance with an alternative embodiment of the present invention. - 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. 2 , each lostmotion system 100 may be disposed between acam 200 and anengine valve 300. Thecams 200 may include one ormore cam lobes motion system 100. The lostmotion system 100 is shown to act on asingle engine valve 300, however, it is appreciated that the lostmotion system 100 may act on more than one engine valve through a valve bridge in alternative embodiments. - In one embodiment of the present invention, as shown in
FIG. 2 , each lostmotion system 100 may include amaster piston 110 hydraulically linked to aslave piston 120 by ahydraulic passage 130. Acontrol valve 150 is disposed in thehydraulic passage 130 so that it may selectively block or unblock the hydraulic passage. Electronic or mechanical control of thecontrol valve 150 permits fluid to enter thehydraulic passage 130 when thecontrol valve 150 is in an open position (as shown). When thecontrol valve 150 is closed (downward as shown inFIG. 2 ), hydraulic fluid is trapped in thepassage 130, thereby hydraulically locking themaster piston 110 to theslave piston 120. Reopening thecontrol valve 150 may also allow fluid in thepassage 130 to be selectively released, thereby unlocking themaster piston 110 from theslave piston 120. - An
optional accumulator piston 160 may assist in maintaining low pressure fluid in the vicinity of thehydraulic passage 130 so that it may be drained and refilled rapidly. Theoptional accumulator piston 160 may be particularly useful when the lostmotion system 100 is used to provide variable valve actuation. In the instances where variable valve actuation is provided, thecontrol valve 150 may be a high-speed trigger valve. High-speed trigger valves may be capable of being opened and closed one or more times per engine cycle to enable locking and unlocking themaster piston 110 from theslave piston 120 one or more times per engine cycle. - Hydraulic fluid may be supplied to the
hydraulic passage 130 by thereservoir system 400. Thereservoir system 400 may include areservoir 410, alow pressure feed 420, anoptional check valve 430, aninlet port 440, anair bleed opening 450, and acommon gallery circuit 460. Hydraulic fluid, such as, for example, engine oil, may be provided from the low pressure feed 420 to thereservoir 410. Theoptional check valve 430 may prevent hydraulic fluid in thereservoir 410 from flowing back to thelow pressure feed 420. - In one embodiment of the present invention, the
reservoir system 400 may include anair bleed opening 450 near the top of thereservoir 410. Theair bleed 450 may allow air entrained in the hydraulic fluid that enters thereservoir 410 from the low pressure feed 420 to exit the system before it enters the one or morelost motion systems 100. Theair bleed opening 450 may be sized to allow small quantities of air to exit from thereservoir system 400 freely, while still offering restriction to the exit of hydraulic fluid, even at relatively high pressure. Theair bleed 450 may also allow air to enter thereservoir 410 to make up for hydraulic fluid that is fed by the reservoir to thegallery circuit 460. This may prevent a vacuum effect from preventing hydraulic fluid from flowing out of thereservoir 410 under a relatively small gravitational force. Still further, theair bleed 450 may permit air that does become entrained in the hydraulic fluid of the lostmotion systems 100 to bubble up and out of these systems over time. - The
inlet port 440 may be located near the top of thereservoir 410. Placement of theinlet port 440 near the top of thereservoir 410 may enhance the ability of thereservoir system 400 to allow air entrained in the fluid provided by the low pressure feed 420 to exit through theair bleed 450. - The
gallery circuit 460 may provide hydraulic fluid from thereservoir system 400 to each of the possible plurality of lostmotion systems 100. Thereservoir system 400 may be located at any point along the expanse of thegallery circuit 460. The upper level of hydraulic fluid in thereservoir 410 may be above the level of thehydraulic passages 130 so that gravity can facilitate the flow of hydraulic fluid from the reservoir to the hydraulic passages. - It is appreciated that in alternative embodiments, more than one reservoir system could be provided to service the lost
motion systems 100 included in the engine. In fact, each lostmotion system 100 may benefit from incorporating areservoir system 400 local to the lost motion system. Theselocal reservoir systems 400 may be integrally incorporated into the housing of each lostmotion system 100. - It is appreciated that the
low pressure feed 420 need not connect directly to thereservoir 410. With reference toFIG. 3 for example, thelow pressure feed 420 may connect to thegallery circuit 460 directly, instead of connecting through thereservoir 410. - In one embodiment, as shown in
FIG. 6 , the lostmotion system 100 may further comprise an optional passage 170 for bypassing thecontrol valve 150, and anoptional check valve 175 disposed in the passage 170. The optional passage 170 andcheck valve 175 may permit hydraulic fluid to enter and refill thehydraulic passage 130 when there is insufficient time to open thecontrol valve 150 between engine valve events, for example, in a variable valve actuation system. - With renewed reference to
FIG. 2 , operation of the lostmotion system 100 may begin by filling thereservoir 410 with hydraulic fluid from thelow pressure feed 420. Theoptional check valve 430 permits hydraulic fluid flow into thereservoir 410 from thelow pressure feed 420, but does not permit a substantial amount of fluid to flow back to the low pressure feed from the reservoir. - As will be apparent to those of ordinary skill in the art, the
control valve 150 may be normally open, or normally closed. For illustrative purposes, as shown inFIG. 2 , an embodiment of the present invention including a normallyopen control valve 150 will be described. Embodiments of the present invention may use either a normally open or a normally closedcontrol valve 150. - At the time that the engine is shut down, the
reservoir 410 may contain a substantial amount of hydraulic fluid. At this time each of thecontrol valves 150 open, thereby connecting thehydraulic passage 130 from thegallery circuit 460 and thereservoir 410, as shown inFIG. 2 . Over time, hydraulic fluid may leak out of thehydraulic passage 130 due to leakage past themaster piston 110 and theslave piston 120. Hydraulic leakage may also occur past theaccumulator 160. Features of various embodiments of the present invention, however, may limit the amount of leakage past these and other system components, which could deplete the level of hydraulic fluid in thereservoir 410. First, theaccumulator 160 may be disposed so that it is inverted as compared to its position shown inFIG. 2 . Theaccumulator 160 position inFIG. 2 is provided for ease of illustration, and is not intended to show the only, or even preferred, positioning of the accumulator. Second, themaster piston 110 and/or theslave piston 120 may be inverted to limit the drainage of hydraulic fluid. Third, thereservoir 410 may be provided with a sufficiently great amount of hydraulic fluid that it will continue to retain a useful amount of fluid over a prolonged period even if a low to moderate level of fluid leakage occurs past theaccumulator 160. Fourth, the bottom of thereservoir 410 may be positioned below the level of thegallery circuit 460 such that the fluid in thereservoir 410 is prevented from being entirely drained out. Fifth, the reservoir feed 440 may be positioned at the top of thereservoir 410 to prevent hydraulic fluid drainage into the engine should thecheck valve 430 fail or be absent. Some, but not necessarily all, embodiments of the present invention may include one or more of these features. - At the time of engine start up, the
hydraulic passage 130 may be so depleted of hydraulic fluid that displacement of themaster piston 110 fails to result in sufficient displacement of theslave piston 120 to produce a desired actuation ofengine valve 300. Hydraulic fluid may be supplied by thereservoir 410 to thehydraulic passage 130 at this time. The supply of fluid to thehydraulic passage 130 may begin by opening thecontrol valve 150. By opening thecontrol valve 150, fluid is permitted to flow from thereservoir 410, through thegallery circuit 460 to thehydraulic passage 130. Thegallery circuit 460 may be located relative to the individual lostmotion systems 100 so that gravity encourages the flow of fluid from the gallery circuit to the individual lost motion systems. - The flow of fluid into each of the
hydraulic passages 130 may be further encouraged by the pumping action of themaster piston 110 in conjunction with selective control of thecontrol valve 150. As themaster piston 110 pumps downward with each revolution of thecam 200, thecontrol valve 150 may be open so that fluid may be drawn into thehydraulic passage 130 by the vacuum created by the master piston. As themaster piston 110 pumps back upward under the influence of the main exhaust lobe on thecam 200, thecontrol valve 150 may be maintained closed so that themaster piston 110 does not drive fluid back out of thehydraulic passage 130. This cycle may be repeated until thepassage 130 andaccumulator 160 are refilled with fluid. - In addition, the high pressure generated in the master-slave circuit may force any air in the circuit out past the close clearance between the
master piston 110 and theslave piston 120 and their respective bores. In one embodiment of the present invention, as shown inFIG. 4 , themaster piston 110 may be disposed in a direction substantially orthogonal or perpendicular to the orientation of theslave piston 120, such that any air in the circuit may be located at the piston/bore interface and may be readily forced out. - An example of the control valve timing that may be used to further enhance the refilling of the lost
motion system 100 is provided inFIG. 5 . The cam may be provided with one or more cam lobes that provide amain exhaust motion 500 and acompression release motion 510, for example. The control valve position may be maintained in an open position until just prior to themain exhaust motion 500. At this time the control valve may be closed, and maintained closed until approximately the mid-point of themain exhaust motion 500, at which time the control valve may be re-opened. This timing may be used during the first part of cranking (engine start-up) to facilitate refilling of the circuits, after which time the normal starting valve motion may be generated. It is contemplated that the control valve timing of embodiments of the present invention may be used in conjunction with other engine valve events, such as, a main intake valve event and an engine braking valve event. - It will be apparent to those skilled in the art that variations and modifications of the present invention can be made without departing from the scope or spirit of the invention. For example, as shown in
FIG. 7 , the one or morelost motion systems 100 may include acollapsible tappet assembly 180 operatively connected to arocker arm 182, which, in turn, is operatively connected to one ormore engine valves 300. Other embodiments of the one or morelost motion systems 100 for selectively losing part or all of the motion imparted to thesystem 100 are considered well within the scope and spirit of the present invention.
Claims (23)
1. A system for supplying hydraulic fluid to one or more lost motion systems in an internal combustion engine, comprising:
a reservoir;
a gallery circuit connected to said reservoir, wherein said gallery circuit is adapted to be connected to the one or more lost motion systems; and
a control valve adapted to provide selective hydraulic communication between said gallery circuit and the one or more lost motion systems.
2. The system of claim 1 further comprising an air bleed opening provided in said reservoir.
3. The system of claim 1 wherein said gallery circuit is disposed relative to the one or more lost motion systems to facilitate the flow of hydraulic fluid from said gallery circuit to the one or more lost motion systems under the influence of gravity.
4. The system of claim 1 wherein said reservoir is disposed relative to the one or more lost motion systems to facilitate the flow of hydraulic fluid from said reservoir to the one or more lost motion systems under the influence of gravity.
5. The system of claim 1 further comprising means for selectively opening said control valve during an engine start up period.
6. The system of claim 1 further comprising a hydraulic fluid supply passage for supplying hydraulic fluid to the reservoir system.
7. The system of claim 6 , wherein said fluid supply passage connects to an inlet port in said reservoir.
8. The system of claim 7 , wherein the inlet port is disposed proximate the top of said reservoir.
9. The system of claim 6 , wherein said fluid supply passage connects to said gallery circuit.
10. The system of claim 6 , a check valve disposed in said fluid supply passage.
11. The system of claim 1 , wherein the lost motion system comprises:
a master piston;
a slave piston; and
a hydraulic passage operatively connecting said master piston to said slave piston.
12. The system of claim 11 , wherein said master piston is disposed in a direction substantially orthogonal to the direction of said slave piston.
13. The system of claim 11 , wherein at least one of said master piston and said slave piston is inverted.
14. The system of claim 11 , further comprising an accumulator piston disposed proximate said hydraulic passage.
15. The system of claim 11 , wherein the level of hydraulic fluid in said reservoir is above the level of said hydraulic passage.
16. The system of claim 11 , further comprising:
a bypass passage providing hydraulic fluid bypass of said control valve; and
a check valve disposed in said bypass passage.
17. A hydraulic actuating system in a multi-cylinder internal combustion engine, said system comprising:
a plurality of lost motion systems, wherein one lost motion system is provided for each cylinder in the multi-cylinder engine;
a reservoir;
a gallery circuit connected to said reservoir, wherein said gallery circuit is adapted to be connected to said plurality of lost motion systems; and
a control valve adapted to provide selective hydraulic communication between said gallery circuit and said plurality of lost motion systems.
18. The system of claim 17 , further comprising means for selectively opening said control valve during an engine start up period.
19. The system of claim 17 , wherein said gallery circuit is disposed relative to said lost motion systems to facilitate the flow of hydraulic fluid from said gallery circuit to said lost motion systems under the influence of gravity.
20. The system of claim 17 , wherein said reservoir is disposed relative to said lost motion systems to facilitate the flow of hydraulic fluid from said reservoir to said lost motion systems under the influence of gravity.
21. A method of providing hydraulic fluid to a lost motion system during start up of an internal combustion engine, said method comprising the steps of:
providing hydraulic fluid in a reservoir, the reservoir being disposed relative to the lost motion system to facilitate the flow of hydraulic fluid to the lost motion system under the influence of gravity;
blocking hydraulic communication between the reservoir and the lost motion system during application of at least an initial portion of an engine valve event motion to the lost motion system; and
providing hydraulic communication between the reservoir and the lost motion system during application of at least a later portion of the engine valve event motion to the lost motion system.
22. The method of claim 21 , wherein the engine valve event comprises a main exhaust event.
23. The method of claim 21 , further comprising the step of venting air from the reservoir through an air bleed opening provided in said reservoir.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/839,143 US20050000476A1 (en) | 2003-05-06 | 2004-05-06 | System and method for improving performance of hydraulic actuating system |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US46808803P | 2003-05-06 | 2003-05-06 | |
US10/839,143 US20050000476A1 (en) | 2003-05-06 | 2004-05-06 | System and method for improving performance of hydraulic actuating system |
Publications (1)
Publication Number | Publication Date |
---|---|
US20050000476A1 true US20050000476A1 (en) | 2005-01-06 |
Family
ID=33452186
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/839,143 Abandoned US20050000476A1 (en) | 2003-05-06 | 2004-05-06 | System and method for improving performance of hydraulic actuating system |
Country Status (5)
Country | Link |
---|---|
US (1) | US20050000476A1 (en) |
EP (1) | EP1623100A4 (en) |
JP (1) | JP2007500314A (en) |
CN (1) | CN1820123A (en) |
WO (1) | WO2004102008A2 (en) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20170081986A1 (en) * | 2015-09-22 | 2017-03-23 | Jacobs Vehicle System, Inc. | Lost motion differential valve actuation |
WO2017190216A1 (en) * | 2016-05-03 | 2017-11-09 | Tonand Inc. | Hydraulic device for variably operating timed components of a combustion engine |
WO2018065010A1 (en) * | 2016-10-05 | 2018-04-12 | Schaeffler Technologies AG & Co. KG | Hydraulics unit for an internal combustion engine with hydraulically variable gas exchange valve gear |
WO2020055924A1 (en) * | 2018-09-10 | 2020-03-19 | Jacobs Vehicle Systems, Inc. | Lost motion variable valve actuation systems and methods |
US20200182105A1 (en) * | 2018-12-11 | 2020-06-11 | Hyundai Motor Company | Oil control valve |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2008248838A (en) * | 2007-03-30 | 2008-10-16 | Man Diesel As | Cam driven exhaust valve operation system for large size two cycle diesel engine |
EP2261471B1 (en) * | 2009-05-25 | 2014-09-17 | C.R.F. Società Consortile per Azioni | Internal combustion engine with two hydraulically actuated intake valves with different return springs for each cylinder |
AU2012355968A1 (en) * | 2011-04-21 | 2013-10-31 | Actuant Corporation | Synchronized lifting apparatus |
FI20135019L (en) * | 2013-01-07 | 2014-07-08 | Waertsilae Finland Oy | Valve lifting device and method for driving a valve lifting device |
ZA201502677B (en) | 2014-04-24 | 2015-12-23 | Harnischfeger Tech Inc | Mining shovel with bushings at pin locations |
GB2559401B (en) | 2017-02-06 | 2020-02-19 | Jaguar Land Rover Ltd | Apparatus and method for a hydraulic valvetrain system |
KR102300677B1 (en) * | 2017-08-03 | 2021-09-08 | 자콥스 비히클 시스템즈, 인코포레이티드. | Systems and Methods for Backflow Management and Sequencing of Valve Motion in Enhanced Engine Braking |
Citations (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2602434A (en) * | 1947-03-29 | 1952-07-08 | Worthington Pump & Mach Corp | Hydraulic valve operating mechanism operable to vary valve lift and valve timing |
US2694387A (en) * | 1944-07-10 | 1954-11-16 | Bendix Aviat Corp | Internal-combustion engine |
US5000145A (en) * | 1989-12-05 | 1991-03-19 | Quenneville Raymond N | Compression release retarding system |
US5327860A (en) * | 1992-10-14 | 1994-07-12 | Volkswagen Ag | Hydraulic tappet-clearance compensating arrangement for a cam-controlled valve lifter |
US5537976A (en) * | 1995-08-08 | 1996-07-23 | Diesel Engine Retarders, Inc. | Four-cycle internal combustion engines with two-cycle compression release braking |
US5537975A (en) * | 1994-10-07 | 1996-07-23 | Diesel Engine Retarders, Inc. | Electronically controlled compression release engine brakes |
US5746175A (en) * | 1995-08-08 | 1998-05-05 | Diesel Engine Retarders, Inc. | Four-cycle internal combustion engines with two-cycle compression release braking |
US6024060A (en) * | 1998-06-05 | 2000-02-15 | Buehrle, Ii; Harry W. | Internal combustion engine valve operating mechanism |
US20020121252A1 (en) * | 2001-03-05 | 2002-09-05 | Natalie Payne | Control system for deactivation of valves in an internal combustion engine |
US6758175B2 (en) * | 2002-10-25 | 2004-07-06 | Delphi Technologies, Inc. | Apparatus for purging and excluding air from a hydraulic manifold assembly for variable deactivation of engine valves |
US6779496B2 (en) * | 2001-01-16 | 2004-08-24 | Robert Bosch Gmbh | Pressure reservoir for exerting pressure on a hydraulic system, with which preferably a gas exchange valve of an internal combustion engine is actuated |
US6907851B2 (en) * | 2002-05-14 | 2005-06-21 | Caterpillar Inc | Engine valve actuation system |
US6941909B2 (en) * | 2003-06-10 | 2005-09-13 | Caterpillar Inc | System and method for actuating an engine valve |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4664070A (en) * | 1985-12-18 | 1987-05-12 | The Jacobs Manufacturing Company | Hydro-mechanical overhead for internal combustion engine |
JPS63176610A (en) * | 1987-01-19 | 1988-07-20 | Honda Motor Co Ltd | Control device for suction and exhaust valves |
DE3929072A1 (en) * | 1989-09-01 | 1991-03-07 | Bosch Gmbh Robert | VALVE CONTROL DEVICE WITH SOLENOID VALVE FOR INTERNAL COMBUSTION ENGINES |
DE3939934A1 (en) * | 1989-12-02 | 1991-06-06 | Man Nutzfahrzeuge Ag | VALVE CONTROL FOR GAS EXCHANGE VALVES OF INTERNAL COMBUSTION ENGINES |
JP4129489B2 (en) * | 1995-08-08 | 2008-08-06 | ジェイコブス ビークル システムズ、インコーポレイテッド | Internal combustion engine having combined control of cam and electrohydraulic engine valve |
JP2001522017A (en) * | 1997-11-04 | 2001-11-13 | ディーゼル エンジン リターダーズ,インコーポレイテッド | Lost motion valve actuation system |
KR20010032344A (en) * | 1997-11-21 | 2001-04-16 | 디이젤 엔진 리타더스, 인코포레이티드 | Method and system start-up apparatus for removing air and debris from a valve actuation system |
US6267098B1 (en) * | 1997-11-24 | 2001-07-31 | Diesel Engine Retarders, Inc. | Valve operating system having full authority lost motion |
GB2348245B (en) * | 1999-03-25 | 2002-10-23 | Ricardo Inc | Valvegear for engines of reciprocating piston type |
EP1232336A4 (en) * | 1999-09-17 | 2009-08-05 | Diesel Engine Retarders Inc | Captive volume accumulator for a lost motion system |
-
2004
- 2004-05-06 CN CNA2004800193850A patent/CN1820123A/en active Pending
- 2004-05-06 US US10/839,143 patent/US20050000476A1/en not_active Abandoned
- 2004-05-06 JP JP2006532573A patent/JP2007500314A/en active Pending
- 2004-05-06 WO PCT/US2004/013936 patent/WO2004102008A2/en active Application Filing
- 2004-05-06 EP EP04751353A patent/EP1623100A4/en not_active Withdrawn
Patent Citations (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2694387A (en) * | 1944-07-10 | 1954-11-16 | Bendix Aviat Corp | Internal-combustion engine |
US2602434A (en) * | 1947-03-29 | 1952-07-08 | Worthington Pump & Mach Corp | Hydraulic valve operating mechanism operable to vary valve lift and valve timing |
US5000145A (en) * | 1989-12-05 | 1991-03-19 | Quenneville Raymond N | Compression release retarding system |
US5327860A (en) * | 1992-10-14 | 1994-07-12 | Volkswagen Ag | Hydraulic tappet-clearance compensating arrangement for a cam-controlled valve lifter |
US5537975A (en) * | 1994-10-07 | 1996-07-23 | Diesel Engine Retarders, Inc. | Electronically controlled compression release engine brakes |
US5746175A (en) * | 1995-08-08 | 1998-05-05 | Diesel Engine Retarders, Inc. | Four-cycle internal combustion engines with two-cycle compression release braking |
US5537976A (en) * | 1995-08-08 | 1996-07-23 | Diesel Engine Retarders, Inc. | Four-cycle internal combustion engines with two-cycle compression release braking |
US6024060A (en) * | 1998-06-05 | 2000-02-15 | Buehrle, Ii; Harry W. | Internal combustion engine valve operating mechanism |
US6779496B2 (en) * | 2001-01-16 | 2004-08-24 | Robert Bosch Gmbh | Pressure reservoir for exerting pressure on a hydraulic system, with which preferably a gas exchange valve of an internal combustion engine is actuated |
US20020121252A1 (en) * | 2001-03-05 | 2002-09-05 | Natalie Payne | Control system for deactivation of valves in an internal combustion engine |
US6907851B2 (en) * | 2002-05-14 | 2005-06-21 | Caterpillar Inc | Engine valve actuation system |
US6758175B2 (en) * | 2002-10-25 | 2004-07-06 | Delphi Technologies, Inc. | Apparatus for purging and excluding air from a hydraulic manifold assembly for variable deactivation of engine valves |
US6941909B2 (en) * | 2003-06-10 | 2005-09-13 | Caterpillar Inc | System and method for actuating an engine valve |
Cited By (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10184363B2 (en) * | 2015-09-22 | 2019-01-22 | Jacobs Vehicle Systems, Inc. | Lost motion differential valve actuation |
US20170081986A1 (en) * | 2015-09-22 | 2017-03-23 | Jacobs Vehicle System, Inc. | Lost motion differential valve actuation |
WO2017190216A1 (en) * | 2016-05-03 | 2017-11-09 | Tonand Inc. | Hydraulic device for variably operating timed components of a combustion engine |
US11187117B2 (en) | 2016-10-05 | 2021-11-30 | Schaeffler Technologies AG & Co. KG | Hydraulics unit for an internal combustion engine with hydraulically variable gas exchange valve gear |
WO2018065010A1 (en) * | 2016-10-05 | 2018-04-12 | Schaeffler Technologies AG & Co. KG | Hydraulics unit for an internal combustion engine with hydraulically variable gas exchange valve gear |
WO2020055924A1 (en) * | 2018-09-10 | 2020-03-19 | Jacobs Vehicle Systems, Inc. | Lost motion variable valve actuation systems and methods |
KR20210045484A (en) * | 2018-09-10 | 2021-04-26 | 자콥스 비히클 시스템즈, 인코포레이티드. | Lost motion variable valve actuation system and method |
CN112912596A (en) * | 2018-09-10 | 2021-06-04 | 雅各布斯车辆系统公司 | Lost motion variable valve actuation system and method |
JP2022500585A (en) * | 2018-09-10 | 2022-01-04 | ジェイコブス ビークル システムズ、インコーポレイテッド | Lost motion variable valve drive system and method |
US11230951B2 (en) | 2018-09-10 | 2022-01-25 | Jacobs Vehicle Systems, Inc. | Lost motion variable valve actuation systems and methods |
EP3850196A4 (en) * | 2018-09-10 | 2023-01-04 | Jacobs Vehicle Systems, Inc. | Lost motion variable valve actuation systems and methods |
JP7241861B2 (en) | 2018-09-10 | 2023-03-17 | ジェイコブス ビークル システムズ、インコーポレイテッド | Lost motion variable valve actuation system and method |
KR102551572B1 (en) * | 2018-09-10 | 2023-07-04 | 자콥스 비히클 시스템즈, 인코포레이티드. | Lost motion variable valve operating system and method |
KR20230101954A (en) * | 2018-09-10 | 2023-07-06 | 자콥스 비히클 시스템즈, 인코포레이티드. | Lost motion variable valve actuation systems and methods |
KR102642043B1 (en) * | 2018-09-10 | 2024-02-27 | 자콥스 비히클 시스템즈, 인코포레이티드. | Lost motion variable valve actuation systems and methods |
US20200182105A1 (en) * | 2018-12-11 | 2020-06-11 | Hyundai Motor Company | Oil control valve |
Also Published As
Publication number | Publication date |
---|---|
CN1820123A (en) | 2006-08-16 |
WO2004102008A3 (en) | 2005-07-14 |
EP1623100A2 (en) | 2006-02-08 |
JP2007500314A (en) | 2007-01-11 |
WO2004102008A2 (en) | 2004-11-25 |
EP1623100A4 (en) | 2008-11-26 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US7500466B2 (en) | Variable valve actuation and engine braking | |
KR101101556B1 (en) | Lost motion system and method for fixed-time valve actuation | |
KR100575042B1 (en) | Engine valve actuation system | |
US6883492B2 (en) | Compact lost motion system for variable valve actuation | |
US7823553B2 (en) | Engine brake having an articulated rocker arm and a rocker shaft mounted housing | |
JP4129490B2 (en) | Engine braking with active valve actuation | |
US5996550A (en) | Applied lost motion for optimization of fixed timed engine brake system | |
JP2010508463A (en) | Engine brake equipment | |
CN103109049A (en) | Combined engine braking and positive power engine lost motion valve actuation system | |
US20050000476A1 (en) | System and method for improving performance of hydraulic actuating system | |
CN102472124A (en) | Lost motion variable valve actuation system with valve catch piston | |
US7059283B2 (en) | System and method of retaining hydraulic fluid in a hydraulic valve actuation system |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: JACOBS VEHICLE SYSTEMS INC., CONNECTICUT Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:VANDERPOEL, RICHARD;REEL/FRAME:015765/0031 Effective date: 20040819 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |