WO1983001485A1

WO1983001485A1 - Multiple concentric intake/exhaust valve system for an internal combustion engine

Info

Publication number: WO1983001485A1
Application number: PCT/US1982/001417
Authority: WO
Inventors: Inc. Alternative Combustion Engineering; Charles S. Bergeron
Original assignee: Alternative Combustion Eng
Priority date: 1981-10-19
Filing date: 1982-10-15
Publication date: 1983-04-28
Also published as: EP0091944B1; DE3278215D1; EP0091944A1; JPS58501832A; EP0091944A4

Abstract

An intake and exhaust valve system deployed in an internal combustion engine that improves available charge flow through the engine, provides improved charge turbulence and swirl of charge during each intake stroke for better mixture, provides for multiple independent fuel mixing at the cylinder (12), allows the use of concentric intake and exhaust valves (22, 24) also providing for balanced charge entry exit symmetry. The intake and exhaust valve system includes using a plurality of two or more concentric valve assemblies per cylinder, each intake valve (22) being mounted within a hollow exhaust valve (24), the multiple intake and exhaust valve (22, 24) providing optimum, flow area entering and exiting the cylinder (12). Two or more charge passage openings (14) per cylinder strategically disposed enhances the uniform distribution of charge per unit time. Utilization of the present invention greatly increases the fuel efficiency of the engine, reduces emission pollution without sacrificing engine horsepower.

Description

MULTIPLE CONCENTRIC INTAKE/EXHAUST VALVE SYSTEM FOR AN INTERNAL COMBUSTION ENGINE BACKGROUND OF THE INVENTION This invention relates generally to an improve- ent for an internal combustion engine, and specifically in the intake and exhaust valve system to enhance the charge volume per unit time for intake and exhaust, and provide other improvements for greatly increasing the efficiency of the engine, the total combustion process and the reduction of pollution.

Attempts have been made in the past to employ what are termed "concentric intake and exhaust valve mechanisms" in internal combustion engines. One example is shown in U. S. Patent 1,350,800 issued to Greuter, August 24, 1920, which shows a single concentric intake and exhaust valve system per cylinder employed to afford greater area for inlet and exhaust ports. In order to attempt to achieve an operational model, Greuter discloses a very complex camming system to insure that the intake and exhaust valves are seated properly. Specifically, cam surfaces are used to close the valve as well as open the valve. The great deficiency of Greuter (apart from the extremely complex and expensive camming system which he finds necessary in order to make his system attempt to work) is the massive weight of the single concentric valve assembly. The excessive surface area of the single concentric valve assembly in the combustion chamber creates extreme loading problems resulting from exhaust compression after the combustion stroke because the exhaust valve must open against high gas pressures in the cylinder. The extremely large surface area pre¬ sented by the single exhaust valve (in conjunction with the surface area of the intake valve) puts great demand on the system, making it impractical of operation. In another system showing a single concentric valve, U. S.

OMPI Patent 1,950,911 issued to Zahodiakin ±n March 13, 1934, the patentee discloses a sleeve-like concentric intake and exhaust valve system to reduce the exhaust gas pres¬ sure on the exhaust valve. Again the system is quite impractical due to the size and mass of the valves pre¬ sented. The deficiencies shown in the prior art amplify and clearly demonstrate problems which have not allowed a concentric valve system to be practical in a conven¬ tional combustion engine.

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.

In the preferred embodiment, 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.

Improved efficiency is attributed to the increased vol¬ ume of charge flow per unit time into the cylinder while improving intake charge velocity. The second effect is that by swirling the charge, a more thorough, homogeneous mixture is achieved in the combustion chamber after the intake stroke. This allows a more complete combustion of the charge, deriving more energy per stroke of combustion.

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.

OMPI SUMMARY OF THE INVENTION

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.

In the preferred embodiment four concentric intake and exhaust valves are employed. Four circular openings are provided through the cylinder head to each combustion chamber. The openings are sized and geometrically arranged relative to each other to achieve an optimum total cir¬ cumferential distance per combustion chamber. The intake valve area opening per unit time when coupled with the optimum intake charge velocity in the port determines the volume of charge received in the cylinder. By increasing the total intake valve circumference per cylinder when compared with the total valve circumference in a conven¬ tional engine, the lift distance required decreases to achieve the same valve opening area. With the lower lift requirement, the time needed to reach optimum valve open¬ ing is decreased. Duration at optimum valve opening is now increased. This results in a larger mass charge vol¬ ume per unit time of the intake stroke.

Each opening in the cylinder head receives a con¬ centric intake and exhaust valve assembly, each of which are described in greater detail below. In particular, 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

OMPI W1PO within a hollow-chambered exhaust valve. 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.

Two types of intake manifolds could be employed.

A single source, centrally located, manifold may be used to equally supply all four intake valves per cylinder. Alternatively, two separate manifolds could use different types of fuels, each independently supplied to the com- bustion chamber.

The use of multiple concentric valve assemblies per cylinder allows for balanced intake charge induction and exhaust impulse expulsion.

The exhaust valve is mounted such that the exhaust outlet port surrounds the exterior of the exhaust valve. The exhaust valve is seated in such a way that upon opening, exhaust will be received into the outlet port around the exterior of the exhaust valve.

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.

Three 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. In one embodiment, 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.

The present intake and exhaust valve system is mounted in an overhead valve arrangement in the engine cylinder head. The cylinder head as on other conven- tional engines is removable from the cylinder block. In essence the pistons, the block, the crank shaft, the rods and the like are conventional and do not form a part of the invention. It is the intake and exhaust valve system (including the valve actuating mechanisms) that forms the invention.

In operation, twin cams (.one on each side of the engine1 can be used to open and close the intake and exhaust valves in their proper sequence. For each cyl¬ inder, there are four intake valves and four exhaust valves (in the preferred embodiment) . By proper selec¬ tion of the cam lobes spacing (relative to the cycle)

OMPI the intake valves can be sequentially opened, rather than opened in unison, to permit the intake of the charge in steps around the upper portion of the cylinder chamber. This can create a swirl effect, caused from the intake valves opening at different times in a particular chamber, thus effecting a more turbulent greater mixing action of the charge with the cylinder. The incoming charge can also act as a cooling agent for the valve assembly in that it passes through the interior of the exhaust valve and over the back face surface of the intake valve.

It is important to realize that in the present sys¬ tem, when compared with some of the prior art concentric valves, the mass of each concentric valve assembly is greatly reduced as is the overall individual inertial effect experienced by the valves during movement. In the prior art, with a single concentric valve assembly encompassing the majority of the combustion chamber, the exhaust gas pressure on the valve faces is too great to germit exhaust valve opening without creating excessive loads on the valve actuating mechanism, greatly dimi¬ nishing the overall efficiency of the system.

It is an object of this invention to provide an im¬ proved -yalve system for an internal combustion engine that enhances the overall efficiency of the engine, re- duces fuel consumption without reducing horsepower, and reduces exhaust emission pollution.

It is an object of this invention to provide in¬ creased duration at optimum valve opening.

It is another object of this invention to provide an improved concentric intake and exhaust valve system for an internal combustion engine that increases the

W1PO available area of optimum intake flow charge per unit time, while reducing inertial loads on the individual concentric valve assemblies.

And 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.

But yet still another object of this invention is to provide an improved intake and exhaust valve system for combustion engines that enhances the efficiency of com¬ bustion by providing swirl of intake charge within the cylinder during intake stroke by sequentially opening the intake valves.

But yet still another object of this invention is to provide an improved intake and exhaust valve system for combustion engines that allows for symmetrical dis¬ position of relative porting and valving within the com¬ bustion chamber surface to provide for balanced entry and exit of charge.

In accordance with these and other objects which will be apparent hereinafter, the instant invention will now be described with particular reference to the ac¬ companying drawings.

BRIEF DESCRIPTION OF THE DRAWINGS

Figure 1 shows a top plan view, partially in phantom, which shows the overhead valve and cam arrangement and the exhaust manifold utilized in the present invention. Figures 2A, and 2B show side elevational views in cross section through a typical cylinder head showing two of four valves deployed in a single combustion cham¬ ber, each of the valves being concentric intake and ex- haust valves in accordance with the present invention. Figure 2A shows a centrally located intake manifold. Figure 2B shows independently disposed fuel source mani¬ folds.

Figure 3 shows a side elevational view as in Figure 2 with the intake valve in an open position.

Figure 4 shows a side elevational view of the present invention as in Figure 3 with the exhaust valve open and the intake valve closed.

Figure 5 shows an exploded view of the intake/ex- haust valve assembly.

Figure 6 shows a side elevational view of an exhaust valve assembly.

PREFERRED EMBODIMENT OF THE INVENTION

Referring now to the drawings and specifically Fig- ure 1 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. Thus for a four cylinder engine as shown, 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).. Note also that the cam sha s 10 have four sets of three lobes at each cylinder sta¬ tion, with the lobes representing an inner lobe 16 for driving the intake valve and two outside lobes 18, which drive the exhaust valve. The cams 10 may be driven in a conventional manner and are mounted with suitable bearings and oil channels and the like which are not shown for the sake of clarity. The arrangement of the cams 10, however, is basically that of an overhead cam engine. Many essential elements of the engine including the intake manifold, the carburetor, oil covers and the like are not shown in the schematic drawing of Figure 1.

Referring now to Figure 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. Note that the valve assembly axes are somewhat offset from the center of the cylinder, and that each valve assembly is angularly aligned at approximately a

30° angle to each other (angle between the intake valve _. stems) . ^{r '}

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. _As 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. With the intake valve 22 open, the inner part of the exhaust valve 24 in conjunc¬ tion with, the intake manifold form an intake passage 30 that allows the charge to flow from atmospheric through the intake manifold and the inner passage of the exhaus _. valve 24 into the cylinder. Note that as shown in Fig¬ ure 3 both intake valves 22 are open at the same time. The actual opening and closing of the intake valves 22 in each cylinder could be staged sequentially during the intake stroke to allow for swirling of the charge into the cylinder. Note also that the intake valve 22 does not need to lift very far from its seat to allow for maximum flow charge capacity (although it is shown ex- aggerated in the drawing) . In each combustion chamber 32 there is a total of four intake valves 22 which open as shown in Figure 3. Thus charge is received through four intake valve openings into a single cylinder 34 providing an optimum amount of charge flow per unit time into the cylinder 34 per unit time. Note however that the intake valve 22 is similar in mass and size to a conventional intake valve.

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. 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. As the cam 10 continues to rotate and the lobes 18 are reducing lift, 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. In addition 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.

Referring back to Figure 1, again it can be seen that 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. Secondly, it can be seen from Figure 1 that by proper degree selection of the cam lobes relative to ramp opening, 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.

Claims

I Claim: - 15 -

1. An intake and exhaust valve system deployed in a four stroke, internal combustion engine for improving intake and exhaust charge volume per unit time in each cylinder comprising:

at least two concentric intake and exhaust valve assemblies mounted in fluid communication with each engine cylinder;

means for opening said intake valve coupled to said intake valves; and

means for opening said exhaust valves coupled to said exhaust valves.

2. A valve system as in Claim 1, including:

a cylinder head, said head having at least two apertures per engine cylinder, each of said apertures re- ceiving a concentric intake and exhaust valve assembly; and

means for mounting each of said intake and exhaust valve assemblies in said cylinder head apertures.

3. A valve system as in Claim 2, wherein:

said cylinder head includes at least one intake charge passage in fluid communication with said intake valves and an exhaust passage in fluid communication with said exhaust valves.

4. A valve system as in Claim 3, including:

means for opening said intake valves sequentially

OMP in time relative to the beginning of the intake stroke thereby producing charge swirl in said cylinder d ring the intake stroke.

5. A valve system as in Claim 2, wherein:

said cylinder head apertures are symetrically dis¬ posed on each side of the central longitudinal axis of said cylinder.

6. A valve system as in Claim 3, including:

a, first charge source coupled in fluid communication with one of said intake valves through a first intake charge passage; and

a second charge source, independent of said first charge source, coupled in fluid communication with a different intake valve, whereby said engine can utilize two different ^"fuels that are mixed after receipt into said cylinder.

7. A valve system as in Claim 1, wherein:

the combined lift and intake valve circumferential distance is determined by the optimum flow charge cap- ability of the port to produce maximum charge volume per unit time for a given cylinder volume.

8. An improved charge induction and exhaust gase ex¬ pulsion system for a reciprocating internal combustion engine, said engine having at least one cylinder com- prising:

an engine housing having at least one cylinder;

O PI first and second charge induction means for intro¬ ducing charge into said cylinder coupled to said cylinder;

first and second exhaust gas expulsion means for expelling exhaust gas from said cylinder coupled to said cylinder;

first and second apertures disposed through said engine housing providing fluid communication from out¬ side said housing into said cylinder, said first charge induction means and said first exhaust gas expulsion means being concentrically disposed in said first aper¬ ture, and said second charge induction means and said second exhaust gas expulsion means being concentrically disposed in said second aperture; and

means for controlling said first and second charge induction means and said first and second exhaust gas expulsion means for regulating the flow of charge into said cylinder and the expulsion of exhaust gas from said cylinder.