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
  • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
  • F01L1/28—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of coaxial valves; characterised by the provision of valves co-operating with both intake and exhaust ports
  • F01L1/285—Coaxial intake and exhaust valves
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
  • F02B75/00—Other engines
  • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
  • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
  • F02B2075/027—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle four

Definitions

• the present invention overcomes the problems of the prior art by providing a multiple, concentric intake and exhaust -valve system for an internal combustion engine. These improvements are, greatly increased volume of charge per unit time when coupled with a cam shaft profile of longer duration of full valve opening over the average range of piston travel, through the engine per intake stroke, while at the same time reducing the mass of each concentric vlave assembly allowing for conventional type cam and lifter action. This greatly reduces the exhaust pressure on each concentric valve assembly, and enhances the swirl characteristics of the charge by providing the., capability of sequential intake of the charge per cyl ⁇ inder by sequentially opening and closing the intake valves in each cylinder.
• four sets of concentric valve assemblies are used per cylinder, which allows for four intake valves and four exhaust valves per cylinder which are disposed to obtain an optimum circumferential valve area for flow into and out of the cylinder.
• Another benefit of the multiple valve intake and exhaust valve system is that one side of the cylinder can be in fluid communication with one fuel source, and at the same time the other side of the cylinder can be in fluid communication with -another fuel source. This allows the mixing of two separate fuels such as gasoline and alcohol in the cylinder.
• Another important result of the inven ⁇ tion is the fact that the increased charge circumferential area available for the intake charge entry and exhaust expulsion which greatly enhances the volume of flow per unit time through the engine) also reduces the mechanical acceleration demands for lifting the intake and exhaust valves. With the greater circumferential distance a- chieved, the valves need be opened less to achieve opti ⁇ mum charge volume per unit time. Duration of optimum valve open position is no longer a limiting factor of camshaft acceleration.
• the primary problem in' conventional, four cycle, internal combustion engines is the inability in the time available per intake stroke to get sufficient charge volume into the cylinder, resulting in low volumetric efficiency in conventional operating RPM ranges.
• the intake charge volume per unit time is conventionally limited by demands of cam ramp acceleration resulting in time limitations on the duration of full valve opening.
• the present invention allows for optimum open valve duration.
• a multiple concentric intake/exhaust valve system for an internal combustion engine which employs at least two or more separate concentric intake and exhaust valves per cylinder to provide increased charge volume per unit time to the cylinder, said intake, exhaust valve system having a lifting mechanism that can achieve optimum flow charge volume per unit time.
• Each opening in the cylinder head receives a con ⁇ centric intake and exhaust valve assembly, each of which are described in greater detail below.
• each intake valve and exhaust valve assembly is similar, so that a single concentric intake and exhaust valve system will be described.
• the intake valve is a conven ⁇ tionally shaped poppet valve which is coaxially located
• the exhaust valye assembly includes a web support having a circular passage that receives and supports the stem of the in ⁇ take valve.
• the exhaust valve being hollow and having the intake valve mounted therein, includes an exhaust valve lifter that contacts a pair of exhaust lobes on the cam shaft Cone lobe that contacts each side of the exhaust valve lifter) to depress exhaust valve driving pins, which are mounted in the main spring support pad.
• the main spring support pad guides the exhaust valve driving pins which in turn engages the exhaust valve assembly.
• a main spring is mounted between the spring retainer and the spring support pad.
• An exhaust valve return spring is mounted between the exhaust valve driving pad and the cylinder head.
• the intake valve may be of conventional weight and size.
• An intake valve lifter contacts the intake lobe of the cam, which is located between the ex ⁇ haust lobes.
• Incoming charge traverses the inside chamber of the exhaust valve.
• the intake valve is seated relative to the exhaust valve around the annular rim on the opposite of the exhaust valve seat.
• cam lobes are presented for each inlet/outlet concentric valve assembly. Dual cams are employed, one ⁇ with each valve train bank mounted overhead on the cyl- inder head.
• the inner cam lobe is used to drive the intake valve against an intake valve lifter disposed on top of the intake valve stem.
• An annular exhaust valve lifter which is in communication with ex ⁇ haust valve driving pins which in turn drive the disc- like exhaust valve driving pad which forms the exhaust valve actuating mechanism.
• Yet another object of this invention is to pro- vide an intake and exhaust valve system that allows for multiple charge sources from different systems simultan ⁇ eously in a given combustion chamber, to allow for mixing at the cylinder.
• Figure 3 shows a side elevational view as in Figure 2 with the intake valve in an open position.
• a top view showing a pair of cam shafts 10 mounted on top of an engine cylinder head 11 is shown, with the engine cylinders 12 dotted and shown in phantom.
• Each cylinder also includes four apertures 14 (shown in phan ⁇ tom), which represent the apertures 14 through the top of the head 11 each of which receives one concentric intake and exhaust assembly.
• each cylinder will have four intake valves and four exhaust valves with the intake valve being disposed concentrically within the exhaust valve (which is described in greater detail below).
• FIG. 2A and 2B a side cross sectional view through two of the intake/exhaust valve assemblies is shown.
• Each of the intake and exhaust valve assemblies functions the same (except for sequen ⁇ tial operation) so that only one will be discussed in detail.
• the valve assembly axes are somewhat offset from the center of the cylinder, and that each valve assembly is angularly aligned at approximately a
• the intake manifold 20 of the embodiment shown in Figure 2A is shown disposed in the center such that it has a split passage from the carburetor where there is a single opening into the carburetor throat terminating with two openings, one at each intake valve 22.
• the intake manifolds 21 of the embodiment shown in Figure 2B is shown one each disposed on the two sides of the cylinder head allowing for two different types of fuels each independently supplied to the cylinder.
• a s shown in this position in Figure 2A and 2B both the intake 22 and exhaust valves 24 are closed or seated. This is the position during compression.
• Figure 3 shows the cam lobes 16 that drive the in- take valves 22 in the maximum lift position depressed against the intake valve lifter 26 which in turn de ⁇ presses the intake valve 22 such that the intake valve is in an optimum open position such as uring the intake stroke (while the exhaust valve 24 is held to its seat in a closed position by the exhaust return springs 50 tension) .
• the intake valve 22 includes a solid stem, a valve head, and a groove near the stem end that re ⁇ ceives a retainer 28 to hold the intake valve 22 in place.
• An intake valve lifter 26 mounted at the top of the intake valve stem 22 in contact with the intake valve cam lobe 16. This pushes down on the stem causing the intake valve 22 to open.
• Figure 4 shows the exhaust valve 24 in the open position during the exhaust stroke to remove exhaust gases from the cylinder 34 after combustion.
• the in ⁇ take valve 22 in this position is closed.
• the exhaust alve 24 is surrounded by an exhaust port 36 that feeds directly to the exhaust manifold 38.
• Each exhaust valve 24 is lifted open by a pair of exhaust lobes 18 on the cam 10 that engage the exhaust valve lifter 40 on each side of the lifter 40 in a bal ⁇ anced or symmetrical fashion.
• the exhaust valve lifter 40 in turn, when forced downwardly against the main spring 42 tension, forces four exhaust valve driving pins 44 (also symmetrically disposed throughout the spring support pad and guide 46) depressing the exhaust valve driving pad 48.
• the exhaust valve driving pad 48 As the exhaust valve driving pad 48 is depressed, the exhaust valve 24 is moved by pres- sure against its inner sleeve, (that also acts as a guide for the intake valve 22) to the open position, as shown in Figure 4. Note that the mass of the exhaust valve 24 and the diameter thereof is quite small when compared to exhaust valves of prior art single concen- trie valve systems.
• the intake valve 22 seat is on the annular rim portion of the exhaust valve 24.
• the exhaust valve 24 must have substantial sealing around it to prevent the leakage of hot exhaust gases in ⁇ to the intake manifold. Annular sealing rings 25 are shown.
• the main spring 42 tension in conjunction with the tension of the exhaust valve return spring 50, cause the exhaust valve 2 to return to its seat in the cylinder head aperture. Every cylinder will include four exhaust valves 24 and four exhaust ports 36 which feed into exhaust manifolds 38 on each side of the engine.
• Figure 5 shows an exploded view of a representative concentric valve assembly.
• the spring tensions of the main spring 42 and the exhaust valve return spring 50 are selected so that the intake valve 22 can open while the exhaust valve 24 remains seated on the aperture such that when the exhaust valve 24 opens, the intake valve 22 re ⁇ mains seated against the exhaust valves combustion cham ⁇ ber face.
• the spring tensions are selected so that no unnecessary vibrations or harmonic actions occur from the rapid reciprocal motions which would force the valves to separate relatively from each other during periods when it is not desirable for either valve to be off its seat.
• each cylinder 12 achieves an optimum combined valve cir ⁇ cumferential distance with optimum valve opening for op ⁇ timum charge flow per unit time relative to the cylinder diameter. This greatly increases the volume of charge flow per unit time through the engine, increasing the overall efficiency as described above.
• the intake valves can be staggered (sequentially opened) during each in ⁇ take stroke. This allows for charge swirl which enhances homogeneous mixing in addition to increased charged flow. This greatly enhances the overall combustion because of the homogeneous distribution of fuel and oxygen molecules throughout the charge and their respective distribution uniformly throughout the combustion chamber at compres ⁇ sion.

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• 1982
  • 1982-10-15 DE DE8282903405T patent/DE3278215D1/de not_active Expired
  • 1982-10-15 JP JP82503423A patent/JPS58501832A/ja active Pending
  • 1982-10-15 WO PCT/US1982/001417 patent/WO1983001485A1/en active IP Right Grant
  • 1982-10-15 EP EP19820903405 patent/EP0091944B1/de not_active Expired

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