EP0685632A1 - Un mécanisme pour suspendre le fonctionnement de soupapes et autres composants de moteurs à combustion interne ou de machines du même genre - Google Patents

Un mécanisme pour suspendre le fonctionnement de soupapes et autres composants de moteurs à combustion interne ou de machines du même genre Download PDF

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Publication number
EP0685632A1
EP0685632A1 EP94107140A EP94107140A EP0685632A1 EP 0685632 A1 EP0685632 A1 EP 0685632A1 EP 94107140 A EP94107140 A EP 94107140A EP 94107140 A EP94107140 A EP 94107140A EP 0685632 A1 EP0685632 A1 EP 0685632A1
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EP
European Patent Office
Prior art keywords
cam
mode
internal combustion
shifter
positions
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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.)
Withdrawn
Application number
EP94107140A
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German (de)
English (en)
Inventor
Vasant Mukund Joshi
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Individual
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Individual
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Publication date
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Priority to EP94107140A priority Critical patent/EP0685632A1/fr
Publication of EP0685632A1 publication Critical patent/EP0685632A1/fr
Withdrawn legal-status Critical Current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
    • F01L13/0005—Deactivating valves

Definitions

  • This invention relates to any engine or machine with cyclically intermittent or reciprocating device operations, and enables selective suspension of these operations over some cycles. It particularly relates to improving the inefficient operations of highly rated vehicle engines under normal partially loaded conditions. Engines modified by this invention produce lesser effluents, have minimized wear, and permit simpler fuel injecting arrangements. Other embodiments of the invention enable dynamic engine braking, multi-fuel operations, and selective operations from any of synchronously coupled prime movers, including another engine or electric motor.
  • crankshaft 1 camshaft 2
  • auxiliary cam 3 mode camshaft 4
  • suction valve rocker 5 exhaust valve rocker 6
  • locking bracket rocker 7 lever 8
  • gears 10 locking bracket 11
  • chain sprockets 12 piston lifters 13, connecting arm 14, bearing block 15, locking pins 16, piston 17, fork 18, piston lever 19, piston lever pivot 20, fork pivot 21, bearings 22, gudgeon pin 23, rocker pivots 24, suction valve 25, exhaust valve 26, guides 27, mode cam 28, locking bracket pivot 29, valve spring 30, bearings 31, cam roller 32, piston lifter spring 33, push rod 34, mode cycle switch 35, locking bracket link 36, locking cams 37, rod bearing 38, shifter cam 39, shifter actuator 40, shifter lever pivot 41, shifter 42, shifter pipe 43, shifter lever 44, cylinders 45, cam follower pivot 46, cam follower 47, thrust bearing 48
  • Figure 1 shows the components relating to one cylinder of the preferred embodiment in the passive operating mode.
  • Figure 2 shows the re-arrangement of the same components in the active operating mode.
  • Figure 3 shows a schematic view of modified engine components showing piston, valve gear, related components, and arrangements for rotation and axial movement of the mode camshaft.
  • Figure 4 shows timings for mode changes.
  • the curves represent: 1) shift register input, 2) outputs from mode cycle switch (solid lines) and shifter switch (dotted lines), 3) solenoid A excitation, 4) solenoid B excitation, 5) shifter lever tilt, 6) mode camshaft axial position, 7) combined auxiliary cam position, 8) position of separate auxiliary cam for exhaust valve, 9) locking bracket lift, 10) locking bracket tilt, 11) suction valve position, 12) exhaust valve position, 13) piston position, 14) camshaft cycle, 15) mode camshaft cycle.
  • the solid and dotted lines represent timings for the first and fourth cylinders, respectively.
  • FIG. 5 shows the logic for excitation of valve solenoids.
  • Figure 6a, 6b and 6c shows typical cross sections of mode cams, shifter cams, and shifter actuator; respectively.
  • Figure 7 shows the assembly of shifter components, and an alternate arrangement for changing modes.
  • Figure 3 shows links 49 connecting the shifter 42 to the sleeve 67 holding thrust bearing 48 mounted on the mode camshaft.
  • Mode camshaft 4 supporting a pin mounted with roller bearings 57 engaging within and driven from slots in the driving sleeve 56 in all axial dispositions, rotates with the driving sleeve at one eighth of the camshaft speed through gears 10.
  • the camshaft rotates at half the crankshaft speed through sprockets 12.
  • Bush bearings 58 facilitate simultaneous rotary and axial movements of the mode camshaft.
  • Figure 4 shows effects of mode changes.
  • individual cylinders change to their passive mode operations from their suction stroke between E3 and F2; and in the second phase of camshaft cycles E to D, individual cylinders change to their active mode operations from their suction stroke between A3 and B2.
  • mode cams change operating modes of individual cylinder devices, in staggered timings, when the devices are inoperative preceding their active timings within the first cycle in the changed operating mode.
  • these timings stagger within a range of 240 to 900 camshaft degrees; within 800 camshaft degrees for the preferred embodiment, corresponding to 100 mode camshaft degrees.
  • each device changes its operating mode in about 30 mode camshaft degrees, during its idle time in the cycle.
  • Shifter lever 44 pivots upon shifter lever pivot 41 on shifter 42, which pivots on shifter pipe 43.
  • Axially movable shifter actuator 40 has two taper keyways on opposite sides, with increasing depths in opposite directions and a parallel keyway to provide anti-rotation within the shifter pipe. Parts of shifter lever enter through holes in the shifter and shifter pipe, to touch the taper keyway bottoms as shown in figure 6c.
  • Mode changes are initiated by solenoid actuation of 5-port direction control valve 66, causing one of pneumatic cylinders 45 to axially move the shifter actuator and thereby rotate the shifter lever upon the shifter lever pivot till such movement is blocked by one of shifter rollers 59 touching one of shifter cams 39 on driving sleeve 56 in the regions around B3 or F3, when changing to the passive or the active mode, respectively (see curve 5, figure 4; and figure 6b).
  • the shifter actuator is in its central position and its further movement is possible only by moving the shifter and the mode camshaft, for which its motive pneumatic force is inadequate.
  • the rising cam profile of the shifter cam lifts the shifter lever with the shifter, upon the shifter pipe to move the mode camshaft axially, through links 49 and thrust bearing 48, in the regions C2 to D3, or G2 to H3 while changing to the passive or the active mode, respectively.
  • This movement ends when the mode camshaft reaches its central position and both the shifter rollers 59 simultaneously contact the shifter cams at their maximum radius in the following D4 to E1, or H4 to A1.
  • D4 to G1, or H4 to C1 while changing to the passive or the active mode, respectively, covering about 100 mode camshaft degrees, all mode cams 28 move their cam followers 47 to change operating modes of all devices.
  • FIG. 6A shows the cross section of one mode cam, and the outlines of other mode cams in relative positions on the mode camshaft.
  • Opposite sectors 1 and 3, of each cam profile have constant radii equal to one of the groove radius and the mode camshaft radius, and are joined by helical sectors 2 and 4.
  • the mode camshaft is shifted between its central and other axial dispositions, within shiftable mode cam positions with every cam follower simultaneously incident upon the sector 1 or 3 of the mode cams of which radius equals the radius of the cylindrical section on its driven side when shifting between the central position and the driven side, and non-driven side when shifting between the central position and the non-driven side.
  • Such shifting of the mode camshaft therefore has no effect on the cam followers.
  • Figure 5 describes the mode changing logic. Signals from potentiometer 50 proportional to accelerator position, and tachogenerator 51 proportional to engine speed, give High output from comparator 52 when engine speed is less than required. Brake switch 63 gives High output on brake application. Shift register 53 gets High input in the absence of acceleration or braking requirements. Mode cycle switch 35 senses a half circular collar on gear 10 giving High output from A1 to E1 of every mode camshaft cycle, as shown by the solid lines in curve 2 of figure 4. Shifter switch 68 senses shifter proximity to give High output in its central position, as shown by the dotted lines in the same curve.
  • Suction valve 25 and exhaust valve 26 are operable by valve cams 65 and locking bracket is operable by locking cams 37 through rockers 5,6, and 7 and levers 8.
  • the auxiliary cams for the suction valve and the looking bracket are combined with one auxiliary cam for the exhaust valve, the latter provided with another auxiliary cam to its valve rocker pivot.
  • Levers are turned upon rockers by the auxiliary cams 3 turning around their respective rocker pivots 24, by rotation of cam followers 47.
  • the auxiliary cams move down the levers on valve rockers 5 and 6 to their active positions of operation by valve cams 65; and in the passive mode, they lift up the levers to their passive positions upon rockers, distant from valve cams.
  • the forked lever on locking bracket rocker 7 has three positions against the locking cams on the camshaft; including a central position where it is inoperable by either locking cam, and one passive and one active end positions arrived by lever movement from the central position caused by movement of the auxiliary cam while changing to the passive or active mode, respectively.
  • the lever In the passive end position, the lever is operable by one locking cam between E2 and E3; and in the active end position, it is operable by the other locking cam between A2 and A3. Either way, the locking cams move the lever back to its central position while the locking bracket toggles from its active to passive position, or passive to active position, respectively.
  • the gudgeon pin has an hour-glass shaped vertical central hole and another axial bore holding both grooved locking pins 16.
  • the bearing block is slideable within bearings in the connecting arm and freely movable within the vertical hole.
  • Fork 18 pivoting on fork pivot 21 in the centre of piston 17 has arms extending through the vertical slots into the push rod bores.
  • Cavities on piston accommodate piston levers 19 pivoting on piston lever pivots 20 on both sides of the fork pivot. Above and below their pivots, one piston lever connects to right-hand and left-hand helical cam faces on one side of the fork, respectively, and the other piston lever connects to left-hand and right-hand helical cam faces on the other side of the fork, respectively.
  • the bottom ends of piston levers enter through longitudinal slots in the gudgeon pin into grooves of locking pins 16.
  • the operating mode of piston changes by one of locking cams 37 operating the forked lever 8, to ultimately operate the fork 16 through locking bracket rocker 7, locking bracket link 36, locking bracket 11, push rods 34, and rod bearings 38.
  • the locking bracket oscillates vertically as shown in curve 9 of figure 4, by its wavy top profile rolling over cam roller 32 by pressure of piston lifter springs 33 through piston lifter pivot 29.
  • the opposite vertical push rod movements caused by rotation of the locking bracket are thus modulated by the oscillatory movements which are equal to the vertical movements of the piston near its top dead centre position. This ensures constant contact of the fork with both rod bearings while it is rotated by their opposite movements.
  • solenoid A initiates the move to the passive operating mode by shifting the mode camshaft to its central position (see figure 4).
  • suction valve rocker In the passive position of its lever, suction valve rocker remains inoperable by its cam keeping the suction valve 25 closed by its spring.
  • the auxiliary cam for the exhaust valve on the suction rocker pivot By turning of the auxiliary cam for the exhaust valve on the suction rocker pivot, its lobe props up the extended projection of the exhaust valve rocker just below its maximum lifted position by the camshaft to keep the exhaust valve partially open throughout the passive mode. Subsequent lifting of the lever on the exhaust valve rocker by the auxiliary cam for the exhaust valve on its rocker pivot, eliminates all rocker operations by camshaft.
  • the locking bracket rocker while moving to its passive position, turns fork 18 over fork pivot 21 causing locking pins 16 to pull out of bearing block 15 and enter holes of the piston lifters 13. Thereafter, piston lifter springs 33 lift the piston lifters along with the piston assembly to a level higher than the top dead centre position of the piston assembly in the active mode. With further movements of the crankshaft, the bearing block slides unobstructed within the swiveling connecting arm.
  • Solenoid B activation Initiates the active operating mode by causing reverse movements of the mode camshaft and auxiliary cams in the same order as when changing to the passive mode. Active operation of suction valves and the piston are followed by active operation of exhaust valves for each cylinder. Piston lifter springs 33 lift the piston lifters, locking bracket, push rods and rod bearings to their topmost positions making the rod bearings and piston lifters inaccessible to the fork and the gudgeon pin, respectively.
  • FIG 7 An alternate embodiment of the invention is shown in figure 7, having the rotary mode camshaft integrated with the driving sleeve.
  • Links 49 connect the shifter to a shifter spindle 60 within tubular cam follower pivot 46.
  • Cam followers 47 pivot upon pins 62 mounted on brackets 61, the latter pivoting on the cam follower pivot and engaging with auxiliary cams as the cam followers of the preferred embodiment.
  • a central arm projecting from each cam follower enters into a groove on the shifter spindle through slots in the brackets and tubular can follower pivot.
  • the components for changing the mode of the exhaust valve can be omitted, including its mode cams, cam follower, the auxiliary cam on the exhaust rocker pivot and its lever, if the exhaust valve rocker is lifted higher by the lobe of the auxiliary cam for the exhaust valve on the suction rocker pivot, in the passive mode, than by the camshaft in the active mode.
  • the exhaust valve can be held closed in the passive mode, like the suction valve.
  • engines are provided with multiple mode camshafts or shifter spindles with independent shifting arrangements, each changing the operating mode of a group of cylinder devices at specific but distinct power levels.
  • shifter cams with N2 lobes are rotated at 2/N2 times the speed of the mode camshaft where N2 is other than 2.
  • shifter actuators are moved by a double acting hydraulic cylinder.
  • a single piston radial pump is operated by two cams on the driving sleeve to pump an amount of oil on one side of the cylinder, in each of the two periods A2-B3 and E2-F3, to move the shifter actuator by half its total stroke each time.
  • a two solenoid 4 port, 3-position hydraulic valve is selectively energised prior to and including these periods, to direct oil to the desired side of the cylinder. When both solenoids are unenergized, the valve poppet returns to its central position where the pumped oil is unloaded to the tank without pressure, and the cylinder ports are closed to retain the position of the shifter actuator.
  • the mode camshaft is shifted through thrust bearings, or the shifter spindle of figure 7 is directly shifted, in two installments by a hydraulic cylinder; in periods C2 to D3 and G2 to H3, in that order when changing to the passive mode, and in the reverse order while changing to the active mode.
  • Another embodiment of an engine controls the operating mode of cylinder valves to provide dynamic braking in a third operating mode.
  • the mode camshaft is shiftable by the shifter cams between five axial positions, instead of the three in the preferred embodiment, after corresponding movement of the shifter actuator.
  • a spring loaded one-armed cam follower follows the mode camshaft profile from one side.
  • Three of the five axial dispositions of the mode camshaft are stable operating mode positions in which the arm connects to the mode camshaft upon cylindrical cross-sections of different diameters, resulting in corresponding stable operating mode positions of the auxiliary cam.
  • the arm moves over four segment mode cams to move the auxiliary cam between these positions.
  • both shifter actuator and mode camshaft are in their central positions.
  • each valve rocker has two levers movable between their active and passive dispositions.
  • Each valve is operable by the valve cam in the four stroke cycle, by the active disposition of the first lever in the active mode position of the auxiliary cam, and by another braking cam on the camshaft by the active disposition of the second lever in the braking mode position of the auxiliary cam.
  • Each valve is inoperable by either cams in the passive mode position of the auxiliary cam. In the braking mode the exhaust valves open in proximity of piston top dead centre position, and the suction valves open in every downward piston stroke, to dissipate energy by compressing air.
  • the mode controlled device is an auxiliary piston entering into the cylinder cavity from the cylinder head in different measures in the active and passive modes, to change the residual volume and compression ratio of the cylinder.
  • engines or machines can be operated with different fuels, variable number of valves, and more importantly, in combination with other prime-movers to include an internal combustion engine or electric motor.
  • a larger engine rotated, with decreased losses in the passive mode, by a secondary smaller engine or an electric motor; is capable of synchronously delivering large amount of power by its active operations, by changing to its active mode.
  • Any machine with cam or crank operated intermittently operating or reciprocating devices can be controlled in the manner described by the invention.
  • Such machines include pumps, rotary internal combustion engines, and industrial machines.
  • Passive mode operations can be delayed, altered or reduced operations of the device, as compared to its active mode operations.
  • the names of parts in this description are only suggestive of their functions and do not restrict their construction or shape.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
EP94107140A 1994-05-06 1994-05-06 Un mécanisme pour suspendre le fonctionnement de soupapes et autres composants de moteurs à combustion interne ou de machines du même genre Withdrawn EP0685632A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP94107140A EP0685632A1 (fr) 1994-05-06 1994-05-06 Un mécanisme pour suspendre le fonctionnement de soupapes et autres composants de moteurs à combustion interne ou de machines du même genre

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Application Number Priority Date Filing Date Title
EP94107140A EP0685632A1 (fr) 1994-05-06 1994-05-06 Un mécanisme pour suspendre le fonctionnement de soupapes et autres composants de moteurs à combustion interne ou de machines du même genre

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EP0685632A1 true EP0685632A1 (fr) 1995-12-06

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EP94107140A Withdrawn EP0685632A1 (fr) 1994-05-06 1994-05-06 Un mécanisme pour suspendre le fonctionnement de soupapes et autres composants de moteurs à combustion interne ou de machines du même genre

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1999047794A1 (fr) * 1998-03-16 1999-09-23 Vasant Joshi Systeme pour desactiver les cames d'un dispositif

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR493221A (fr) * 1917-12-06 1919-08-02 Schneider & Cie Dispositif pour la mise en fonctionnement ou hors d'action de soupapes ou autres organes de distribution
EP0216647A1 (fr) * 1985-08-05 1987-04-01 Automobiles Peugeot Dispositif de commande de soupapes d'un moteur à combustion interne par culbuteurs désactivables
EP0235981A1 (fr) * 1986-02-28 1987-09-09 General Motors Corporation Mécanisme de commande de soupape avec levée et calage variables

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR493221A (fr) * 1917-12-06 1919-08-02 Schneider & Cie Dispositif pour la mise en fonctionnement ou hors d'action de soupapes ou autres organes de distribution
EP0216647A1 (fr) * 1985-08-05 1987-04-01 Automobiles Peugeot Dispositif de commande de soupapes d'un moteur à combustion interne par culbuteurs désactivables
EP0235981A1 (fr) * 1986-02-28 1987-09-09 General Motors Corporation Mécanisme de commande de soupape avec levée et calage variables

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1999047794A1 (fr) * 1998-03-16 1999-09-23 Vasant Joshi Systeme pour desactiver les cames d'un dispositif

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