Ultra high compression tools

Because of the straightline motion imparted to the piston 17, sidewall pressure by the piston 17 on the chamber sidewalls of the cylinder 11 is eliminated, which reduces debilitating friction and preserves the cylinder wall oil film. Much greater compression ratios are achievable with any power input by the driveshaft 22, since combustion pressure is distributed on two crankshaft means, instead of one as is conventional, and due to the elimination of cylinder sidewall friction.

The relative eccentricity of the eccentric arm 28 relative to the linear axis of the disc 21 may be varied in order to tailor the timing of the piston stroke. Accordingly, as shown in FIG. As shown in the drawings, this angle is set to preferably be about 40 degrees of the full circle of crankshaft means rotation.

This inventive arrangement boosts the horsepower and efficiency of the engine 10, since a higher compression is achieved in the cylinder. The compression stage is enhanced by a longer period of dwell time afforded the piston at top dead center by virtue of the eccentric rotation of the cam discs 21 as shown in FIG.

Due to the use of eccentrically rotated discs in this embodiment, much shorter piston strokes can be utilized to achieve greater rpm without increasing piston speed. The higher achievable compression renders an internal combustion engine adapted with the inventive arrangement to run with virtually any fuel, such as liquid, powder, or gas, that can be injected to burn completely at top dead center, since the higher achievable compressions also raise the working space temperature to significantly higher levels.

This would also make possible use of the inventively adapted engine to run on a hydrogen-oxygen reaction. Since the drive trains 24 of both crankshaft means are geared together by the balance gears 31, an idler gear 32, as shown in FIG.

An additional power take-off may be taken from either crankshaft means since both drive trains 24 are co-balanced and co-rotating. The arrangement of the first embodiment may be used to operate a single piston as shown or operate a pair of opposed pistons connected with the translator element The construction of the engine 10 and translator element 18 is similar to that of the first embodiment, such that like reference numerals are used and repeated features will not again be described.

This second embodiment of the invention utilizes a modified drive train crankshaft means for effecting the true straightline motion of the translator element 18 along the longitudinal axes of the cylinder spaces 12 contained in the directly opposed cylinders As in the case of the first embodiment, a pair of oppositely rotatable crankshaft means are disposed on opposed sides of the longitudinal axes of the opposed cylinder spaces Since the construction of each crankshaft is identical, only one will be described with reference to FIG.

The modified drive train labeled 24' commences with the pick-up gear 25 in the manner of the first embodiment. The pick-up gear 25 is keyed for rotation on a linearly directed shaft 36 which rotates a crankshaft piece 37 having a linearly directed crosspiece offset from the axis of rotation of the shaft 36 and extending through the plane of the translator element The base 20 of the translator element 18 is formed with a circular hollow space 39 in which the crankshaft crosspiece 38 is rotated.

Here, a pair of connecting rods 40 are disposed on opposed sides of the translator element base 20, journaled for rotation at their lower ends about the axis of the crosspiece 38 and journaled for rotation at their upper ends on a common pin 41 journaled linearly through the translator base wall While an opposed pair of connecting rods 40 are illustrated associated with each crankshaft piece, it will be understood that a single rod 40 may be used or that a U-shaped piece having its base end journaled on the crosspiece 38 and its arms journaled at opposed ends of the pin 41 may be used instead of two separate rods.

The crankshaft piece 37 operates in the manner of the eccentric arm 28 described above and the connecting rod assembly 40,41 serves as the cam means in place of the eccentrically rotated discs 21 described above. The crankshaft 37 is connected for rotation at its end opposite the shaft 36 with a further shaft 42 disposed for rotation about the same axis of rotation as the shaft 36 and having a diameter identical to the shaft The shaft 42 serves to rotate the balance gear As in the manner of the first embodiment, portions 25 and of the drive train 24' serve as a crankshaft means by which rotational movement of the driveshaft 22 is imparted as solely linear back and forth motion to the translator element 18 and the pistons 17 in true straightline fashion along the longitudinal axis of the directly opposed cylinder chambers The features and advantage of the first embodiment also apply to this second embodiment.

However, to vary the timing in the piston operation, the designer adjusts the position at which the connecting rod pin 41 is disposed through the translator base 20 relative to the longitudinal axis of the opposed cylinder chambers 12 and along an imaginary horizontal line SL perpendicular to the cylinder axis.

As in the case of the first embodiment, the crankshaft means of the drive train pairs 24' are oppositely rotating and disposed on opposed sides of the cylinder chamber longitudinal axis, equadistantly spaced from that longitudinal axis.

The location of the pins 41 are set to be equadistantly spaced from the longitudinal axis of the cylinder chambers 12 along the line SL; however, that distance may be selected as necessary to be closer to or further from the longitudinal axis, as shown in FIGS.

Each slider element 45 is disposed for lateral movement perpendicular to the longitudinal axis of the cylinder chambers 12 within a laterally directed track space 46 formed in the base portion 20 of the translator element The crankshaft means in this embodiment are likewise oppositely rotating and disposed on opposed sides of the longitudinal axis of the opposed cylinder chambers This transmission arrangement also causes the translator element 18 and the pistons 17 to be imparted with back and forth movement in a true straightline motion along the longitudinal axis of the opposed cylinder chambers 12, affording the above-described advantages in operation of the engine This system is especially practical for pistons operated in straightline motion since it is necessary that the fastening devices associated with the piston head be accessible and removable in a direction parallel with the longitudinal axis of the cylinder.

In accordance with this piston removal invention, a cylinder 50 defines a cylinder chamber 51 in which a piston 52 is disposed on the free end of a translator mechanism 53 for imparting back and forth reciprocal motion to the piston in the cylinder, preferably in a straightline fashion along the longitudinal axis of the cylinder. The piston 52 is formed with a central recess 54 defined by serrated longitudinal sidewalls extending inward from the upper surface of the piston.

Extending longitudinally through the piston from the bottom of the recess 54 is a threaded bore 55 communicating at its open lower end with a connector portion of the translator mechanism The connector portion of the translator 53 has a threaded bore 56 aligned with the longitudinal axis of the piston bore 55, such that a bolt 57 can be easily passed through the piston threaded bore 55 into engagement with the translator threaded passage The enlarged head of the bolt 57 presses against the bottom wall of the piston recess 54 upon tightening of the bolt 57 so as to removably fasten the piston 52 to the translator In order to permit removal of the piston out of the cylinder, the head plate of the cylinder 58 is made removable along the longitudinal axis of the cylinder.

The normal cylinder head plate 58 is replaced by a special mounting plate 59, which may be fastened by bolts across the top of the cylinder 50 as shown in FIGS.

The mounting plate 59 is formed with a centrally disposed longitudinally extending passage defined by a sidewall 60 formed with exterior serrations for lockingly engaging the piston recess sidewall serrations to hold the piston 52 against twisting in the cylinder chamber.

At this step of the piston removal operation, the piston 52 is preferably disposed at its top dead center position in the cylinder. A wrench 61, such as a socket wrench, is passed longitudinally through the top of the cylinder 50 and through the interior of the mounting plate passage to engage with the head of the bolt This development was made possible by support from VESA, and I want to thank them for backing this effort.

The Video Electronics Standards Association VESA is an international, non-profit standards association representing a global network of more than hardware, software, computer, display and component manufacturers committed to developing and promoting the electronics industry.

DisplayPort utilizes a state-of-the-art digital protocol and provides an expandable foundation to enable astonishing digital display experiences. All other trademarks, service marks, registered trademarks, and registered service marks are the property of their respective owners.

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