US3809033A - Rocker arm engine brake system - Google Patents

Rocker arm engine brake system Download PDF

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Publication number
US3809033A
US3809033A US00270698A US27069872A US3809033A US 3809033 A US3809033 A US 3809033A US 00270698 A US00270698 A US 00270698A US 27069872 A US27069872 A US 27069872A US 3809033 A US3809033 A US 3809033A
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Prior art keywords
rocker arm
valve
bore
piston
conduit
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Expired - Lifetime
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US00270698A
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English (en)
Inventor
C Cartledge
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Jacobs Vehicle Systems Inc
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Jacobs Manufacturing Co
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Publication date
Application filed by Jacobs Manufacturing Co filed Critical Jacobs Manufacturing Co
Priority to US00270698A priority Critical patent/US3809033A/en
Priority to JP48051566A priority patent/JPS4957216A/ja
Priority to AU56020/73A priority patent/AU465235B2/en
Priority to CA172,924A priority patent/CA985586A/en
Priority to GB2697473A priority patent/GB1373327A/en
Priority to FR7321225A priority patent/FR2192601A5/fr
Priority to CH867273A priority patent/CH574045A5/xx
Priority to DE19732334711 priority patent/DE2334711A1/de
Priority to SE7309687A priority patent/SE381705B/xx
Application granted granted Critical
Publication of US3809033A publication Critical patent/US3809033A/en
Priority to CA228,953A priority patent/CA987978A/en
Assigned to CGG HOLDINGS CORP. reassignment CGG HOLDINGS CORP. MORTGAGE (SEE DOCUMENT FOR DETAILS). Assignors: JACOBS MANUFACTURING COMPANY, THE
Assigned to JACOBS BRAKE TECHNOLOGY CORPORATION reassignment JACOBS BRAKE TECHNOLOGY CORPORATION LICENSE (SEE DOCUMENT FOR DETAILS). Assignors: JACOBS MANUFACTURING COMPANY, 22 E. DUDLEY TOWN RD., BLOOMFIELD, CT. 06002, A CORP. OF NJ.
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • 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
    • F01L13/06—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for braking

Definitions

  • ROCKER ARM ENGINE BRAKE SYSTEM [75] Inventor: Charles F. Cartledge, West Hartford, Conn.
  • ABSTRACT A rocker arm engine brake system for an internal combustion engine in which a rocker arm is movable by a cam operating off the cam shaft to open the exhaust valve of a cylinder at the usual time in the piston cycle; and when it is desired to retard the speed of the engine, a lash piston in the rocker arm is hydraulically extensible at the will of the operator to take up the usual lash between the rocker arm and the exhaust valve so as to enable an auxiliary cam operating off the cam shaft to effectively cooperate with the rocker arm to open the exhaust valve at a time toward the end of a compression stroke of the piston so as to dissipate the energy of gases of compression from acting upon the piston.
  • Separate passages in the rocker arm shaft are utilized for providing fluid for operating the lash piston and for general lubrication. The passages are interconnected by bleed holes. Selective control of the hydraulic system is obtained by means of a solenoid operable valve.
  • the objective of the present invention is to provide a device of this lash piston type having an improved hydraulic system for operating the lash piston.
  • a feature of this improved system lies in the manner in which the rocker arm shaft is utilized for supplying crankcase oil for general lubricating purposes and for also supplying crankcase oil for operating the lash piston.
  • Another feature of this improved system lies in the structured arrangement of the passages for the hydraulic feed whereby undesirable air bubbles are relieved from the system.
  • an internal combustion engine including a piston cylinder served by an exhaust valve, a rocker arm pivotable about a rocker arm shaft against the valve to force the valve to open condition, pedestal means supporting the shaft upon the engine, rotating cam means having periodic cooperation with the rocker arm to pivot it relative to the valve but disabled because of loss motion existing between the rocker arm and the valve from pivoting the rocker arm sufficiently to force the valve to open condition, and selectively operable means for taking up the loss motion so as to remove said disability of the cam means, the selectively operable means comprising a lash piston in a bore of the rocker arm having a retracted condition in which said loss motion exists and having a projected condition in which the loss motion is taken up, an hydraulic circuit for feeding pressurized fluid to the bore to project the lash piston, and selectively operable control valve means in the circuit for controlling flow of said fluid in the circuit, wherein the shaft is formed with a pair of longitudinally extending conduits, a first one of
  • FIG. 1 is a top plan view of a section of a rocker arm shaft of an internal combustion diesel engine in which the invention is embodied;
  • FIG. 2 is a section on line 22 of FIG. 1 directed to the solenoid valve control unit incorporated in a supporting pedestal of the rocker arm shaft;
  • FIG. 3 is an enlarged fragmentary portion of FIG. 2 showing the moved position of the solenoid valve following enerization of the solenoid;
  • FIG. 4 is a section taken on line 44 of FIG. 1 showing the relation of an exhaust rocker arm to the exhaust valves of one of the cylinders of the engine;
  • FIG. 5 is an enlarged detail showing the follower end of the push rod of FIG. 4 in association with a cam element carried by the engines cam shaft;
  • FIG. 6 is an enlarged detail of the rocker arm shown in FIG. 4 with portions cut away;
  • FIG. 7 is a section taken on line 77 of FIG. 6 illustrating the normal position of the combined shuttle and check valve unit
  • FIG. 8 is an enlarged detail illustrating the moved condition of the combined shuttle and check valve unit shown in FIG. 7;
  • FIG. 9 is a view corresponding to that of FIG. 6 of a modified embodiment but illustrating the arrangement in the hydraulicsystem of the shuttle and check valves as separate elements;
  • FIG. 10 is a section on line 10-10 of FIG. 9 illustrating the arrangement of the shuttle and check valves.
  • FIG. 1 l is a view corresponding to that of FIG. 4 but showing an embodiment in which the rocker arm arm overlies a single exhaust valve. 7
  • FIGS. 1-8 DESCRIPTION OF A PREFERRED EMBODIMENT (FIGS. 1-8) Reference is directed to the several FIGURES of the accompanying drawing, and now especially to FIGS. 1-8, wherein the invention is illustrated as incorporated in an internal combustion diesel engine in association with one of its cylinders 10 (FIG. 4).
  • the piston 11 operating in the cylinder is of the four-stroke cycle type. Only so much of the engine needed for an understanding of the invention is described. Accordingly, no description is made of the usual fuel injector and air intake mechanism associated with the cylinder.
  • the cylinder is served by a pair of exhaust valves 12 which are normally held closed, as in FIG. 4, by the usual valve springs 13.
  • An exhaust valve actuating bridge 14 spanning the stems 15 of both valves is actuable by an overhead rocker arm 16 to force the valves to open condition.
  • the bridge is slidably supported upon a stud 17, anchored in the cylinder head 18 in such manner as to allow axial sliding movement of the bridge relative to the valves.
  • the rocker arm is pivoted between its ends upon a stationary rocker arm shaft 21 which is supported by pedestal means 22 (FIG. 1) bolted atop the cylinder head.
  • One end of the rocker arm is located above the central area of the bridge 14 and an opposite end overlies a push rod 24.
  • the rocker arm is pivotable by the push rod relative to the bridge upon cooperation of a rotating cam element 25 (FIG. with the push rod.
  • the push rod is provided with a' boot or follower 26 which rides the periphery of the cam element.
  • the cam element is carried by the usual cam shaft 27.
  • the latter is drivably connected in conventional manner to the usual crankshaft of the engine.
  • the cam element 25 has a main cam rise or lobe 28 on its periphery which is cooperable with the push rod at the usual time in the piston cycle to open the exhaust valves. There. is also provided on the periphery of the cam element in angular space relation to the rise 28 an auxiliary or second cam rise 29 of smaller or lesser radial extent than that of the main rise 28. It is cooperable with the push rod to pivot the rocker arm relative to the bridge 14 at a time near the end of the compression stroke of the piston.
  • the auxiliary cam rise is obtained by undercutting the base circle of the cam element as indicated by the broken line 30.
  • the timing of the cooperation of the respective cam rises with the push rod is determined by the angular position given to the cam rises relative to each other and by the angular disposition of the cam element 25 upon the cam shaft 27 Normally, the cooperation of the auxiliary cam rise with the push rod is ineffective to cause movement of the bridge to open the exhaust valves because of the usual slight lash or loss motion existing between the rocker arm and the bridge.
  • the lash in the rocker arm be taken up so that the exhaust valves will be caused to open through the action of the auxiliary cam rise 29 at or near. the end of the compression stroke so I as to relieve the cylinder of the driving energy of compressed gases.
  • a lash piston 31 (FIGS. 4, 6, 7) is provided in a bore 32 of the rocker arm 16. It is arranged to be operable upon demand of the operator to move outwardly of the rocker arm into pressed relation with the valve bridge so as to take up the lash in the rocker arm.
  • the lash piston is located in the rocker arm above the central area of the valve bridge. It is normally held seated against the bottom of its bore by the biasing force of a return spring 33.
  • the spring is of U-form (FIG. 7), having a bridge piece 34 fastened to the underside of an ear 36 of the rocker arm, and having a pair of parallel spring legs 35. One of the legs extends across a flat at one side of an externally projecting portion of the piston, and the other leg extends across a similar flat at the opposite side of the piston.
  • the spring legs exert a biasing force upon overhead shoulders 37, defined by the flats of the piston, which force normally seats the piston in its bore.
  • the spring legs also cooperate with the flats to prevent turning of the piston in its bore.
  • the lash piston is hydraulically movable at the election of the operator outwardly of the rocker arm against the bias of the return spring 33 to take up the lash between the rocker arm and the bridge.
  • the hydraulic system whereby oil is fed from the engines crankcase to operate the lash piston, and whereby the spent oil is subsequently returned to the crankcase when the braking operation is terminated, represents an advantageous feature of the invention.
  • the hydraulic system includes a solenoid control valve unit 38 (FIGS. 1-3), shown here as mounted in the pedestal 22. It may, however, be mounted in any convenient location suitable for the purposes intended; for example, on an end of the rocker arm shaft, or outside of the engine.
  • the unit is operable by means of a switch, schematically indicated at 39. The latter may be located in the instrument panel for manual operation,
  • the valve unit includes a solenoid spool valve 40 which has a normal position, as in FIG. 2, blocking operating oil flow from the crankcase to the lash piston.
  • Conduit 48 has been provided by inserting a spring partition strip 49 axially into the usual center hole of the rocker arm shaft so as to divide the hole into a pair of longitudinally extending conduits 48 and 51.
  • Coriduit 48 is utilized for conducting oil to operate the lash piston; whereas conduit 51 is used for conducting a supply of oil for lubricating purposes.
  • Conduit 51 is connected by an individual supply passage 52 with the crankcase. Oil is pumped from the crankcase in usual manner through passage 52 into conduit 51. The oil flowing in conduit 51 passes through various bleed holes in the rocker arm shaft, one being shown at 53 (FIG. 6), to lubricate the rocker arm and the push rod.
  • Conduits 48 andSl are sealed at opposite ends from one another. 1
  • Pressurized oil entering conduit 48 flows out of a port 54 (FIGS. 6-8) in the wall of ,the rocker arm shaft to a passage 55 in the rocker arm connecting at 56 to one end of a shuttle valve chamber 57 in the rocker arm.
  • An opposite open end of the valve chamber is covered by a drain plate 58 having a groove defining a relief port 59 exiting at the uppermost area of the rocker arm, as best seen in FIG. 6.
  • a port6l intermediately of the ends of the valve chamber leads to an area at the back or upper end of the bore 32 of the lash piston.
  • a combined shuttle valve and check valveunit 62 operable in the valve chamber 57 controls flow of pressure oil to force the lash piston 31 downward and outwardly of the rocker arm againstthe valve bridge 14 to take up the existing lash in the rocker arm. It also controls subsequent relief of such oilto the drain port 59 so as to enable the lash piston to be returned by its spring 33 to normal condition, as in FIG. 6, seated at the back of its bore 32.
  • a shuttle valve member 63 of the combined valve unit has a cylindrical body provided with an axial bore in which a seat 64 for a ball check valve 65 is fitted.
  • a return spring 66 normally holds the check valve seated so as to block communication of an inlet passage 67 through the check valve with side ports 68 opening through the mid-area of the body of the shuttle valve.
  • the shuttle valve has a normal position, under the bias of a return spring 69 (as in FIG. 7) wherein its side ports are blocked by the wall of the valve chamber from communicating with the port 61 leading to the area at the back of the lash piston.
  • the shuttle valve has an opposite or moved position (as in FIG.
  • Pressurized oil flowing in passage 55 from the rocker arm shaft to the end 56 of the shuttle valve chamber 57 moves the valve against the bias of its return spring 69 to register its side ports 68 with the port 61, as in FIG. 8. With this action, the pressurized oil passes through the seat of the ball check valve 65 to the back of the lash piston 31 and forces the latter down against the valve bridge 14.
  • the oil pressure acting upon the lash piston is adequate to move the piston against the force of its return spring 33 sufficiently to take up the existing lash, but is inadequate to cause the valve bridge to open the exhaust valves.
  • the solenoid valve unit 38 As long as the solenoid valve unit 38 is energized to maintain the oil pressure against the lash portion, the latter retains its displaced condition and is hydraulically locked by means of the one-way check valve 65 from returning to its normal condition.
  • the rocker arm is subsequently pivoted by the auxiliary cam rise 29, as well as by the main cam rise 28, it acts through the extended lash piston, pressing against thevalve bridge to open the exhaust valves.
  • the exhaust valves will be opened at the usual time in the cycle through the camming action of the main cam rise 28 with the push rod and will also be opened near the end of the compression stroke through the camming action of theauxiliary cam rise 29 with the push rod.
  • the solenoid control valve unit 38 When it is desired to convert the engine from braking operation back to normal power operation, the solenoid control valve unit 38 is deenergized by the operator. The solenoid spring 41 then returns the solenoid valve to its normal or off position (FIG. 2), in which position the inlet ports 44 of the unit are blocked from the valve ports 45 and the latter communicate around the lower end of the solenoid valve with a drain port 70.
  • the solenoid valve unit Upon deenerigization of the solenoid valve unit, the pressure of oil filling the passageways 46, 48 and 55 between the solenoid valve outlets 45 and the area 56 at the back of the shuttle valve chamber is relieved as the oil spills over through the solenoid ports 45 to the drain port 70. Oil issuing from the latter drops to the cylinder head or deck 18 and finds its way in conventional manner back to the crankcase 43.
  • a desirable advantage of the hydraulic system lies in its capacity to purge itself of air and air bubbles, especially in the passage 61 between the shuttle valve 63 and the bore 32 of the lash piston. It is to be noted in this respect that, when the oil pressure in the passages 46, 48, 55 between the solenoid valve 38 and the chamber 57 of the shuttle valve unit is relaxed, the check valve 65 is caused to close by its spring 66 and the pressure of oil at the rear of the lash piston is relieved through the drain port 59.
  • the latter port is located at the upper most area of the rocker arm at a level above that of the bore 32 of the lash piston and above the level of the horizontally disposed shuttle valve chamber 57, as best seen in FIG. 6.
  • the hydraulic circuit area between the shuttle valve and the bore 32 of the lash piston remains at all times filled with oil. If any air bubbles should find their way to the circuit area beyond the check valve 65, they will rise upwardly through the oil to escape through the drain port 59. Air bubbles are undesirable in the circuit area beyond the check valve when the lash piston has been hydraulically extended since they are subject to compression and may cause the piston to be correspondingly retracted into its bore when the rocker arm is actuated by the auxiliary cam rise. This retraction'or spongy action of the lash piston could result in a failure of the rocker arm to adequately open the exhaust valves.
  • a further advantage of the hydraulic system is that no undesirable pumping action of the lash piston takes place relative to its bore 31 after the braking operation has been terminated. This is because the piston is held retracted and seated at the bottom of its bore by the return spring 33 and is, accordingly, solidly backed each time it is pressed by the rocker arm against the valve bridge during power operation of the engine. Nor is there any pumping action of the lash piston during the braking operation since it is hydraulically locked outwardly in its extendedcondition.
  • Air is also constantly being urged or driven from the conduit 48 during the time that the solenoid unit is deenergized.
  • Conduit 48 is'being constantly primed and flushed during this period with oil bleeding into it from conduit 51 through bleed holes 50 in the partition strip 49, one being shown in FIG. 6.
  • Oil pumped from the crankcase is constantly being circulated through conduit 51 for lubricating purposes.
  • rocker arm shaft may be designed for this purpose having a pair of separate longitudinal extending holes therein interconnected with one another by bleed holes.
  • the shuttle and check valves 63, 65 are shown in FIGS. 7 and 8 as combined into a unit or one-piece arrangement.
  • 64a is located in a branch 74 of passage 73, and it normally blocks passage 73 from a passage 75 connected with a passage 76 leading to the back of the bore 32a of the lash piston 31a.
  • the shuttle valve 63a is a solid member or slug slidable in a second branch 77 of the passage 73. This second branch 77 normally communicates the back of the piston bore 32a from passages 76 and 78 with a drain passage 79.
  • rocker arm assembly as described above in the foregoing embodiments, could be associated with the exhaust valves of each cylinder of the engine; and that all of the exhaust valve rocker arms pivoted upon the rocker arm shaft 21 could be controlled by but one solenoid control valve unit since the conduit 48 in the rocker arm shaft would be common to and serve the several rocker arms pivoted upon the shaft, and the conduit 51 would be common to the several rocker arms for lubricating purposes.
  • An internal combustion engine including a piston cylinder served by an exhaust valve, a rocker arm pivotable about a rocker arm shaft against the valve to force the valve to open condition, means supporting the shaft upon the engine, rotating cam means having periodic cooperation with the rocker arm to pivot it relative to the valve but disabled because of loss motion existing between the rocker arm and the valve from pivoting the rocker arm sufficiently to force the valve .to open condition, and selectively operable means for taking up the loss motion so as to remove said disability of the cam means, the selectively operable means commeans with passage means in the rocker arm leading to the bore of the lash piston, and the second one of the conduits having lateral lube ports through the wall of the shaft and connected for receiving oil feed from the engines crankcase, the conduits being interconnected by bleed holes, the control valve means having a closed normal position blocking feeding of hydraulic fluid into the first conduit and allowing relief of hydraulic fluid from the first conduit to a relief port, and having an open operated position allowing feed of hydraulic fluid into the first conduit and blocking escape of hydraulic fluid from the first
  • An internal combustion engine including a piston cylinder served by an exhaust valve, a rocker arm pivotable about a rocker arm shaft against the valve to force the valve to open condition, means supporting the shaft upon the engine, rotating cam means having periodic cooperation with the rocker arm to pivot it relative to the valve but disabled because of loss motion existing between the rocker arm and the valve from pivoting the rocker arm sufficiently to force the valve to open condition, and selectively operable means for taking up the loss motion so as to remove said disability of the cam means, the selectively operable means comprising a lash piston in a bore of the rocker arm having a retracted condition in which said loss motion exists and having a projected condition in which the loss motion is taken up, a hydraulic circuit for feeding hydraulic fluid to the bore to project the lash piston, and selectively operable control valve means in the circuit for controlling flow of said fluid in the circuit, wherein the shaft is formed with a pair of separate longitudinally extending conduits, a first one of the conduits being part of said circuit and connecting the control valve means with passage means in the rock
  • An internal combustion engine including a piston I cylinder served by an exhaust valve, a rocker arm pivotable about a rocker arm shaft against the valve to force the valve to open condition, means supporting the shaft upon the engine, rotating cam means having periodic cooperation with the rocker arm to pivot it relative to the valve but disabled because of loss motion existing between the rocker arm and the valve from pivoting the rocker arm sufficiently to force the valve to open condition, and selectively operable means for taking up the loss motion so as to remove said disability of the cam means, the selectively operable means comprising a lash piston in a bore of the rocker arm having a retracted condition in which said loss motion exists and having a projected condition in which the loss motion is taken up, a hydraulic circuit for feeding hydraulic fluid to the bore to project the lashpiston, and selectively operable control valve means in the circuit for controlling flow of said fluid in the circuit, wherein the shaft is formed with a pair of separate longitudinally extending conduits, a first one of the conduits being part of said circuit and connecting the control valve means with passage means
  • An internal combustion engine including a piston cylinder served by an exhaust valve, a rocker arm pivotable about a rocker arm shaft against the valve to force the valve to open condition, means supporting the shaft upon the engine, rotating cam means having periodic cooperation with the rocker arm to pivot it relative to the valve but disabled because of loss motion existing between the rocker arm and the valve from pivoting the rocker arm sufficiently to force the valve to open condition, and selectively operable means for taking up the loss motion so as to remove said disability of the cam means, the selectively operable means comprising a lash piston in a bore of the rocker arm having a retracted condition in which said loss motion exists and having-a projected condition in which the loss motion is taken up, a hydraulic circuit for feeding hydraulic fluid to the bore to project the lash piston, and selectively operable control valve means in the circuit for controlling flow of said fluid in the circuit, wherein the shaft is formed with a pair of separate longitudinally extending conduits, a first one of the conduits being part of said circuit and connecting the control valve means with passage means in the rock
  • An internal combustion engine including a piston cylinder served by an exhaust valve, a rocker arm pivotable about a rocker arm shaft against the valve to force the valve to open condition, means supporting the shaft upon the engine, rotating cam means having periodic cooperation with the rocker arm to pivot it relative to the valve but disabled because of loss motion existing between the rocker arm and the valve from pivoting the rocker arm sufficiently to force the valve to open condition, and selectively operable means for taking up the loss motion so as to remove said disability of the cam means, the selectively operable means comprising a lash piston in a bore of the rocker arm having a retracted condition in which said loss motion exists and having a projected condition in which the loss motion is taken up, an hydraulic circuit for feeding hydraulic fluid to the bore to project the lash piston, and selectively operable control valve means in the circuit for controlling flow of said fluid in the circuit; wherein the shaft is formed with a pair of separate longitudinally extending conduits, a first one of the conduits being part of said circuit and connecting the control valve means with passage means in the rocker
  • An internal combustion engine including a piston cylinder served by an exhaust valve, a rocker arm pivotable about a rocker arm shaft against the valve to force the valve to open condition, means supporting the shaft upon the engine, rotating cam means having periodic cooperation with the rocker arm to pivot it relative to the valve but disabled because of loss motion existing between the rocker arm and the valve from pivoting the rocker arm sufficiently to force the valve to open condition, and selectively operable means for taking up'the loss motion so as to remove said disability of the cam means, the selectively operable means comprising a lash piston in a bore of the rocker arm having a retracted condition in which said loss motion exists and having a projected condition in which the loss motion is taken up, an hydraulic circuit for feeding hydraulic fluid to the bore to project the lash piston, and selectively operable control valve means in the circuit for controlling flow of said fluid in the'circuit; wherein the shaft is formed with a pair of separate longitudinally extending conduits, a vfirst one of the conduits being part of said circuit and connecting the control valve means with
  • An internal combustion engine including a piston cylinder served by an exhaust valve, a rocker arm pivotable about a rocker arm shaft against the valve to force the valve to open condition, means supporting the shaft upon the engine, rotating cam means having periodic cooperation with the rocker arm to pivot it relative to the valve but disabled because of loss motion existing between the rocker arm and the valve from pivoting the rocker arm sufficiently to force the valve to open condition, and selectively operable means for taking up the loss motion so as to remove said disability of the cam means, the selectively operable means comprising a lash piston in a bore of the rocker arm having a retracted condition in which said loss motion exists and having a projected condition in which the loss motion is taken up, an hydraulic circuit for feeding hydraulic fluid to the bore to project the lash piston, and selectively operable control valve means in the circuit for controlling flow of said fluid in the circuit; wherein the shaft is formed with a pair of separate longitudinally extending conduits, a first one of the conduits being part of said circuit and connecting the control valve means with passage means in the rocker
  • drain port is at a level above that of the bore of the lash piston and the passage means.
  • a unit comprising a one way check valve member combined with a shuttle valve member is positioned in the rocker arm in the passage means between the control valve means and the bore of the lash piston, the unit having a normal position upon a relaxed fluid pressure condition existing in the passage means upstream of the unit, in which normal position the bore of the lash piston is in communication with a drain port and is blocked by the shuttle valve member from communication with the check valve member.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
US00270698A 1972-07-11 1972-07-11 Rocker arm engine brake system Expired - Lifetime US3809033A (en)

Priority Applications (10)

Application Number Priority Date Filing Date Title
US00270698A US3809033A (en) 1972-07-11 1972-07-11 Rocker arm engine brake system
JP48051566A JPS4957216A (fr) 1972-07-11 1973-05-09
AU56020/73A AU465235B2 (en) 1972-07-11 1973-05-23 Rocker arm engine brake system
CA172,924A CA985586A (en) 1972-07-11 1973-05-30 Rocker arm engine brake system
GB2697473A GB1373327A (en) 1972-07-11 1973-06-06 Rocker arm engine brake system
FR7321225A FR2192601A5 (fr) 1972-07-11 1973-06-12
CH867273A CH574045A5 (fr) 1972-07-11 1973-06-15
DE19732334711 DE2334711A1 (de) 1972-07-11 1973-07-07 Kipphebel-maschinenbremsvorrichtung zur verwendung in einer brennkraftmaschine
SE7309687A SE381705B (sv) 1972-07-11 1973-07-10 Anordning med svengbar arm att bromsa en motor, vilken er av typen med invendig forbrenning
CA228,953A CA987978A (en) 1972-07-11 1975-06-10 Rocker arm engine brake system

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US00270698A US3809033A (en) 1972-07-11 1972-07-11 Rocker arm engine brake system

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US3809033A true US3809033A (en) 1974-05-07

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Application Number Title Priority Date Filing Date
US00270698A Expired - Lifetime US3809033A (en) 1972-07-11 1972-07-11 Rocker arm engine brake system

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US (1) US3809033A (fr)
JP (1) JPS4957216A (fr)
AU (1) AU465235B2 (fr)
CA (1) CA985586A (fr)
CH (1) CH574045A5 (fr)
DE (1) DE2334711A1 (fr)
FR (1) FR2192601A5 (fr)
GB (1) GB1373327A (fr)
SE (1) SE381705B (fr)

Cited By (64)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4173209A (en) * 1977-07-14 1979-11-06 Jordan Edgar R Engine control system and valve deactivator thereof
US4175534A (en) * 1977-07-14 1979-11-27 Edgar R Jordan Valve deactivator for internal combustion engines
US4398510A (en) * 1978-11-06 1983-08-16 The Jacobs Manufacturing Company Timing mechanism for engine brake
US4510900A (en) * 1982-12-09 1985-04-16 The Jacobs Manufacturing Company Hydraulic pulse engine retarder
US4523551A (en) * 1983-05-11 1985-06-18 Aisin Seiki Kabushiki Kaisha Valve actuating device
US4592319A (en) * 1985-08-09 1986-06-03 The Jacobs Manufacturing Company Engine retarding method and apparatus
US4664070A (en) * 1985-12-18 1987-05-12 The Jacobs Manufacturing Company Hydro-mechanical overhead for internal combustion engine
US4688384A (en) * 1985-04-15 1987-08-25 The Jacobs Manufacturing Company Braking boost pressure modulator and method
US4711210A (en) * 1986-12-29 1987-12-08 Cummins Engine Company, Inc. Compression braking system for an internal combustion engine
US4930463A (en) * 1989-04-18 1990-06-05 Hare Sr Nicholas S Electro-rheological valve control mechanism
US5014829A (en) * 1989-04-18 1991-05-14 Hare Sr Nicholas S Electro-rheological shock absorber
US5103779A (en) * 1989-04-18 1992-04-14 Hare Sr Nicholas S Electro-rheological valve control mechanism
US5158109A (en) * 1989-04-18 1992-10-27 Hare Sr Nicholas S Electro-rheological valve
US5526784A (en) * 1994-08-04 1996-06-18 Caterpillar Inc. Simultaneous exhaust valve opening braking system
US5537976A (en) * 1995-08-08 1996-07-23 Diesel Engine Retarders, Inc. Four-cycle internal combustion engines with two-cycle compression release braking
US5540201A (en) * 1994-07-29 1996-07-30 Caterpillar Inc. Engine compression braking apparatus and method
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DE102010011454A1 (de) 2010-03-15 2011-09-15 Schaeffler Technologies Gmbh & Co. Kg Hubkolbenbrennkraftmaschine mit Dekompressionsmotorbremse
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WO2012109780A1 (fr) 2011-02-15 2012-08-23 奚勇 Procédé et dispositif de repositionnement d'une tige de soupape faisant appel à un frein moteur
WO2012155315A1 (fr) 2011-05-18 2012-11-22 上海尤顺汽车部件有限公司 Procédé et dispositif de freinage de culbuteur de type à réinitialisation
CN102003239B (zh) * 2009-08-31 2012-11-28 上海尤顺汽车部件有限公司 一种快速制动的发动机制动装置
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EP3012440A1 (fr) 2010-07-27 2016-04-27 Jacobs Vehicle Systems, Inc. Freinage de moteur combiné et système d'actionnement de soupape à mouvement à vide
US20160298508A1 (en) * 2013-11-13 2016-10-13 Daimler Ag Engine Compression Brake Device for an Internal Combustion Engine
CN106321183A (zh) * 2016-08-17 2017-01-11 潍柴动力股份有限公司 发动机制动执行机构及发动机
CN106382140A (zh) * 2016-10-21 2017-02-08 东风商用车有限公司 一种发动机制动控制油路结构
ITUB20155428A1 (it) * 2015-11-10 2017-05-10 Streparava S P A Con Socio Unico Un dispositivo di controllo di una valvola di un motore a combustione interna per controllare la valvola di un motore a combustione interna
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US10450908B2 (en) * 2014-09-18 2019-10-22 Eaton Intelligent Power Limited Rocker arm assembly for engine braking
US10526926B2 (en) 2015-05-18 2020-01-07 Eaton Srl Rocker arm having oil release valve that operates as an accumulator
US10767522B2 (en) * 2018-04-04 2020-09-08 Pacbrake Company Lost motion exhaust rocker engine brake system with actuation solenoid valve and method of operation
CN112253274A (zh) * 2020-09-11 2021-01-22 浙江九隆机械有限公司 一种制动摇臂
KR20210044292A (ko) * 2018-09-17 2021-04-22 자콥스 비히클 시스템즈, 인코포레이티드. 로스트 모션 밸브 트레인에서 개선된 응답 시간
EP4018080A4 (fr) * 2019-10-15 2023-11-15 Cummins, Inc. Système d'ouverture de soupape d'échappement

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US4523551A (en) * 1983-05-11 1985-06-18 Aisin Seiki Kabushiki Kaisha Valve actuating device
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AU578204B2 (en) * 1985-08-09 1988-10-13 Jacobs Manufacturing Company, The Exhaust brake
US4592319A (en) * 1985-08-09 1986-06-03 The Jacobs Manufacturing Company Engine retarding method and apparatus
US4664070A (en) * 1985-12-18 1987-05-12 The Jacobs Manufacturing Company Hydro-mechanical overhead for internal combustion engine
US4711210A (en) * 1986-12-29 1987-12-08 Cummins Engine Company, Inc. Compression braking system for an internal combustion engine
US4930463A (en) * 1989-04-18 1990-06-05 Hare Sr Nicholas S Electro-rheological valve control mechanism
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US5540201A (en) * 1994-07-29 1996-07-30 Caterpillar Inc. Engine compression braking apparatus and method
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US5526784A (en) * 1994-08-04 1996-06-18 Caterpillar Inc. Simultaneous exhaust valve opening braking system
US5890469A (en) * 1995-03-20 1999-04-06 Ab Volvo Exhaust valve mechanism in an internal combustion engine
WO1996029508A1 (fr) * 1995-03-20 1996-09-26 Ab Volvo Mecanisme de soupape d'echappement pour un moteur a combustion interne
US5829397A (en) * 1995-08-08 1998-11-03 Diesel Engine Retarders, Inc. System and method for controlling the amount of lost motion between an engine valve and a valve actuation means
US5746175A (en) * 1995-08-08 1998-05-05 Diesel Engine Retarders, Inc. Four-cycle internal combustion engines with two-cycle compression release braking
US5680841A (en) * 1995-08-08 1997-10-28 Diesel Engine Retarders, Inc. Internal combustion engines with combined cam and electro-hydraulic engine valve control
US5839453A (en) * 1995-08-08 1998-11-24 Diesel Engine Retarders, Inc. Internal combustion engines with combined cam and electro-hydraulic engine valve control
US5537976A (en) * 1995-08-08 1996-07-23 Diesel Engine Retarders, Inc. Four-cycle internal combustion engines with two-cycle compression release braking
US5794589A (en) * 1995-11-24 1998-08-18 Ab Volvo Exhaust valve mechanism in an internal combustion engine
WO1998007965A1 (fr) * 1996-08-22 1998-02-26 Diesel Engine Retarders, Inc. Systeme et methode de reglage d'une soupape de moteur
US6647954B2 (en) 1997-11-17 2003-11-18 Diesel Engine Retarders, Inc. Method and system of improving engine braking by variable valve actuation
WO1999051864A3 (fr) * 1998-04-03 1999-12-23 Diesel Engine Retarders Inc Rattrapeur de jeu hydraulique a frein de decompression
US6718940B2 (en) 1998-04-03 2004-04-13 Diesel Engine Retarders, Inc. Hydraulic lash adjuster with compression release brake
WO1999051864A2 (fr) * 1998-04-03 1999-10-14 Diesel Engine Retarders, Inc. Rattrapeur de jeu hydraulique a frein de decompression
US6234143B1 (en) 1999-07-19 2001-05-22 Mack Trucks, Inc. Engine exhaust brake having a single valve actuation
WO2001018373A1 (fr) * 1999-09-10 2001-03-15 Diesel Engine Retarders, Inc. Systeme culbuteur a perte de mouvement muni d'un frein par compression integre
US6422186B1 (en) 1999-09-10 2002-07-23 Diesel Engine Retarders, Inc. Lost motion rocker arm system with integrated compression brake
EP1222375A4 (fr) * 1999-09-17 2009-06-03 Diesel Engine Retarders Inc Frein a culbuteur a perte de mouvement integre avec soupape de commande d'arret/remise en position a perte de mouvement
US6591795B2 (en) 1999-09-17 2003-07-15 Diesel Engine Retarders, Inc. Captive volume accumulator for a lost motion system
US6394067B1 (en) 1999-09-17 2002-05-28 Diesel Engine Retardersk, Inc. Apparatus and method to supply oil, and activate rocker brake for multi-cylinder retarding
US6415752B1 (en) 1999-09-17 2002-07-09 Diesel Engine Retarders, Inc. Captive volume accumulator for a lost motion system
EP1222375A1 (fr) * 1999-09-17 2002-07-17 Diesel Engine Retarders, Inc. Frein a culbuteur a perte de mouvement integre avec soupape de commande d'arret/remise en position a perte de mouvement
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US6450144B2 (en) 1999-12-20 2002-09-17 Diesel Engine Retarders, Inc. Method and apparatus for hydraulic clip and reset of engine brake systems utilizing lost motion
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US6253730B1 (en) 2000-01-14 2001-07-03 Cummins Engine Company, Inc. Engine compression braking system with integral rocker lever and reset valve
US6213091B1 (en) 2000-03-21 2001-04-10 Deere & Company Engine compression brake system
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EP1549831A4 (fr) * 2002-09-19 2008-01-23 Diesel Engine Retarders Inc Systeme et procede a deplacement a vide pour actionner une soupape a temps fixes
US20050217623A1 (en) * 2004-04-02 2005-10-06 Ronald Truelove Cam follower
US7392777B2 (en) 2005-08-27 2008-07-01 Schaeffler Kg Variable valve train of an internal combustion engine
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US7556004B2 (en) * 2006-10-16 2009-07-07 Caterpillar Inc. Bactrian rocker arm and engine using same
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US8210144B2 (en) 2008-05-21 2012-07-03 Caterpillar Inc. Valve bridge having a centrally positioned hydraulic lash adjuster
US20090288626A1 (en) * 2008-05-21 2009-11-26 Caterpillar Inc. Valve bridge having a centrally positioned hydraulic lash adjuster
US20100006063A1 (en) * 2008-07-11 2010-01-14 Hans-Werner Dilly Internal Combustion Engine Having an Engine Brake Device
US8225769B2 (en) * 2008-07-11 2012-07-24 Man Truck & Bus Ag Internal combustion engine having an engine brake device
US7984705B2 (en) 2009-01-05 2011-07-26 Zhou Yang Engine braking apparatus with two-level pressure control valves
CN102003239B (zh) * 2009-08-31 2012-11-28 上海尤顺汽车部件有限公司 一种快速制动的发动机制动装置
DE102010011454B4 (de) 2010-03-15 2020-08-06 Schaeffler Technologies AG & Co. KG Hubkolbenbrennkraftmaschine mit Dekompressionsmotorbremse
DE102010011454A1 (de) 2010-03-15 2011-09-15 Schaeffler Technologies Gmbh & Co. Kg Hubkolbenbrennkraftmaschine mit Dekompressionsmotorbremse
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US8813719B2 (en) 2010-03-15 2014-08-26 Schaeffler Technologies Gmbh & Co. Kg Internal combustion piston engine with a compression relief engine brake
US20110220052A1 (en) * 2010-03-15 2011-09-15 Schaeffler Technologies Gmbh & Co. Kg Internal combustion piston engine with an adjustable inflating element
US20110220062A1 (en) * 2010-03-15 2011-09-15 Schaeffler Technologies Gmbh & Co. Kg Internal combustion piston engine with a compression relief engine brake
CN103228876A (zh) * 2010-04-05 2013-07-31 雅各布斯车辆***公司 结合有发动机气门致动***或发动机制动器的摇臂轴底座
CN107829791A (zh) * 2010-07-27 2018-03-23 雅各布斯车辆***公司 组合发动机制动和正功率发动机空动阀致动***
EP3012440A1 (fr) 2010-07-27 2016-04-27 Jacobs Vehicle Systems, Inc. Freinage de moteur combiné et système d'actionnement de soupape à mouvement à vide
CN107829791B (zh) * 2010-07-27 2021-01-05 雅各布斯车辆***公司 组合发动机制动和正功率发动机空动阀致动***
WO2012109780A1 (fr) 2011-02-15 2012-08-23 奚勇 Procédé et dispositif de repositionnement d'une tige de soupape faisant appel à un frein moteur
WO2012155315A1 (fr) 2011-05-18 2012-11-22 上海尤顺汽车部件有限公司 Procédé et dispositif de freinage de culbuteur de type à réinitialisation
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US9512746B2 (en) 2013-12-05 2016-12-06 Jacobs Vehicle Systems, Inc. Apparatus and system comprising collapsing and extending mechanisms for actuating engine valves
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WO2015085206A1 (fr) * 2013-12-05 2015-06-11 Jacobs Vehicle Systems, Inc. Appareil et système comprenant des mécanismes d'affaissement et d'extension pour actionner des soupapes de moteur
CN105579674B (zh) * 2013-12-05 2018-04-13 雅各布斯车辆***公司 用于驱动发动机气门的、包括收缩和延伸机构的装置和***
EP2975230A1 (fr) 2014-07-15 2016-01-20 Jacobs Vehicle Systems, Inc. Systèmes d'actionnement de soupape à mouvement perdu avec des éléments de verrouillage comprenant des éléments de verrouillage en forme de coin
US11225887B2 (en) 2014-09-18 2022-01-18 Eaton Intelligent Power Limited Rocker arm assembly for engine braking
US10450908B2 (en) * 2014-09-18 2019-10-22 Eaton Intelligent Power Limited Rocker arm assembly for engine braking
US10526926B2 (en) 2015-05-18 2020-01-07 Eaton Srl Rocker arm having oil release valve that operates as an accumulator
ITUB20155428A1 (it) * 2015-11-10 2017-05-10 Streparava S P A Con Socio Unico Un dispositivo di controllo di una valvola di un motore a combustione interna per controllare la valvola di un motore a combustione interna
CN106321183A (zh) * 2016-08-17 2017-01-11 潍柴动力股份有限公司 发动机制动执行机构及发动机
CN106382140A (zh) * 2016-10-21 2017-02-08 东风商用车有限公司 一种发动机制动控制油路结构
WO2019028424A1 (fr) 2017-08-03 2019-02-07 Jacobs Vehicle Systems, Inc. Systèmes et procédés de gestion de contre-courant et de séquençage de mouvement de soupape dans un freinage moteur amélioré
WO2019028428A1 (fr) 2017-08-03 2019-02-07 Jacobs Vehicle Systems, Inc. Systèmes et procédés de gestion de contre-courant et de mise en séquence de mouvements de soupape dans un freinage moteur amélioré
US11242778B2 (en) * 2018-04-04 2022-02-08 Pacbrake Company Lost motion exhaust rocker engine brake system with actuation solenoid valve and method of operation
US10767522B2 (en) * 2018-04-04 2020-09-08 Pacbrake Company Lost motion exhaust rocker engine brake system with actuation solenoid valve and method of operation
KR20210044292A (ko) * 2018-09-17 2021-04-22 자콥스 비히클 시스템즈, 인코포레이티드. 로스트 모션 밸브 트레인에서 개선된 응답 시간
CN112789393A (zh) * 2018-09-17 2021-05-11 雅各布斯车辆***公司 改善的空程阀机构的响应时间
EP3853450A4 (fr) * 2018-09-17 2022-06-15 Jacobs Vehicle Systems, Inc. Temps de réponse amélioré dans des trains de soupapes à mouvement perdu
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CN112789393B (zh) * 2018-09-17 2023-08-04 雅各布斯车辆***公司 改善的空程阀机构的响应时间
EP4018080A4 (fr) * 2019-10-15 2023-11-15 Cummins, Inc. Système d'ouverture de soupape d'échappement
CN112253274A (zh) * 2020-09-11 2021-01-22 浙江九隆机械有限公司 一种制动摇臂
CN112253274B (zh) * 2020-09-11 2022-02-18 浙江九隆机械有限公司 一种制动摇臂

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SE381705B (sv) 1975-12-15
FR2192601A5 (fr) 1974-02-08
DE2334711A1 (de) 1974-01-24
CH574045A5 (fr) 1976-03-31
AU465235B2 (en) 1975-09-18
AU5602073A (en) 1974-11-28
JPS4957216A (fr) 1974-06-04
CA985586A (en) 1976-03-16
GB1373327A (en) 1974-11-13

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