WO1997001026A1

WO1997001026A1 - Process and apparatus for sequential breathing

Info

Publication number: WO1997001026A1
Application number: PCT/US1996/010793
Authority: WO
Inventors: Martin C. Fields
Original assignee: Individual
Current assignee: Individual
Priority date: 1995-06-23
Filing date: 1996-06-24
Publication date: 1997-01-09
Anticipated expiration: 1997-12-23
Also published as: AU6674596A

Abstract

Intake and exhaust manifolds (300, 300c) include a plurality of interconnected furcation members (312, 304a, 304b) wherein each furcation member defines a primary passage (318) that branches into secondary passages (310, 314). The furcation members are arranged in levels such that the number of passages within a manifold decrease in levels more fluidly distant from the machine associated therewith. Each first level furcation member (304) defines two secondary passages (306, 308) that are individually in fluid communication with working chambers of a machine that includes a plurality of sequentially pulsing work chambers (c1-c4). Each secondary passage (306, 308) of a first level furcation member individually extends toward and fluidly communicates with a working chamber that pulses half way through the operating order from the working chamber that the other secondary passage of that first level furcation member extends toward and fluidly communicates with. Throughout the manifolds, the secondary passages (306, 308) of a representative furcation member each have an identical, yet out of phase, pulse interval.

Description

PROCESS AND APPARATUS FOR SEQUENTIAL BREATHING

FIELD OF THE INVENTION

The present invention relates generally to the field of machines with multiple working chambers, and more particularly to the breathing of reciprocating pumps and the breathing, compression and expansion combustion cycles of multi-cylinder internal combustion engines. DESCRIPTION OF THE PRIOR ART

Machines with multiple working chambers typically include manifolds that direct fluid into and out of the working chambers. One type of such machines is a multi-cylinder internal combustion engine. In a representative internal combustion engine, gasses that support combustion flow towards the cylinder chambers of the engine through an intake manifold. Post combustion gasses flow away from the cylinder chambers of the engine through an exhaust manifold. Fluid communication between each cylinder chamber and the intake manifold and exhaust manifold is typically by way of a cylinder inlet port and outlet port, respectively.

In certain engines, such as four stroke engines, the flow through each inlet port is regulated by an inlet valve or valves, while the flow through each outlet port is regulated by an outlet valve or valves. The valves open to provide fluid communication and close to terminate fluid communication. The opening and closing of the valves is synchronized with the proper positioning of pistons within the cylinder chambers and the ignition of fuel within the cylinder chambers. The pistons reciprocate and are connected by connecting rods to a crankshaft that rotates in response to the reciprocation of the pistons. The crankshaft is typically linked to a camshaft or camshafts that rotate to facilitate proper opening and closing of the valves. In certain engines, such as some two stroke engines, mechanically operated valves such as those described above are not employed. Rather, in some cases a cylinder becomes in fluid communication with a manifold when the piston therein moves to expose a cylinder port, which is sometimes equipped with a reed valve or the like.

While the fundamentals of internal combustion engine operation have not changed drastically over the decades, there has always been a desire to increase the efficiency and power of internal combustion engines. The desire for greater efficiency and power increases constantly as the cost of fuel and the consequences of pollution increase. It has been long recognized that various manifold arrangements can have a substantial impact upon the efficiency and power of internal combustion engines. Accordingly, numerous improvements have been made to the manifolds of internal combustion engines, and numerous ones of those improvements have been patented. Many of the previously patented improvements address the advantages of minimizing flow losses (i.e., pumping losses) through manifolds. While certain internal combustion engine and manifold designs have reduced pumping losses, additional reduction in pumping losses would further increase the efficiency and power of multi-cylinder machines such as multi-cylinder internal combustion engines. Further, conventional manifolds do not necessarily establish equivalent cycle to cycle breathing characteristics for each cylinder of a multi- cylinder internal combustion engine. Such variations in cycle to cycle breathing result in uneven and often excessive combustion within cylinders, resulting in roughly running engines that must be structurally designed to compensate for the excessive combustion. Such over-designing increases the costs of engines. SUMMARY OF THE INVENTION

The present invention relates to improvements in machines with multiple working chambers such as, but not limited to, multi-cylinder internal combustion engines. More particularly, methods and apparatus are provided that enhance the breathing of multi-cylinder internal combustion engines. Further, the methods and apparatus of the present invention equalize the breathing of cylinders of a multi-cylinder internal combustion engine. Further, the methods and apparatuε of the present invention equalize the cycle to cycle combustion within cylinders of a multi-cylinder internal combustion engine. In accordance with the most preferred embodiments of the present invention, the broad concepts of the present invention relate to both the intake and exhaust of gasses from internal combustion engines. Thus, in accordance with preferred embodiments of the present invention, the present invention applies to both intake and exhaust manifolds. Thus, unless it is specified or readily apparent to be otherwise, the entirety of thiε disclosure should be considered to apply to both intake manifolds and exhaust manifolds, and the processes associated with each.

In accordance with the preferred embodiments of the present invention, intake and exhaust manifolds are provided which include a plurality of uniquely arranged and furcated pasεages. The furcated pasεages are arranged in a manner such that the volumes of a gas travailing therethrough cooperate to enhance pumping efficiency. Also, in accordance with the preferred embodiments of the present invention, the furcated passages are arranged εuch that intake back- flows generated at one cylinder enhance the breathing of another cylinder, and exhauεt furcated paεεageε are arranged to eliminate backflow and locally reduce pressure to enhance the breathing cylinders.

In accordance with the preferred embodiments of the present invention, pairs of cylinderε of an internal combustion engine that are fired half way through the firing order from one another breathe through a common bifurcation member. Each of the cylinders that are so paired preferably breathe in through an intake bifurcation member and breathe out through a separate exhaust bifurcation. For each of the cylinders that are so paired, each of the bifurcation members associated therewith defines three passages that communicate at and extend from a common location within the bifurcation member. The three passages of a representative bifurcation member include a primary passage that branches into two secondary passages. A first secondary passage of the representative bifurcation member connects to and communicates with the port of a first cylinder of the pair of cylinders, and a second secondary passage of the representative bifurcation member connects to and communicates with the port of a second cylinder of the pair of cylinders. The primary passage of the representative bifurcation member is preferably connected to and communicates with a similar primary passage of another bifurcation member that is associated with another pair of cylinders.

In accordance with the preferred embodiments of the present invention, internal combustion engines having an even number of cylinders that fire sequentially are preferably employed. Further, it is preferred that the cylinders not only fire sequentially, but that they also fire in an even frequency interval meaning that the crankshaft rotates the same angular distance between each successive cylinder firing. This meanε that at a constant engine speed, an equal amount of time passes between each successive cylinder firing. However, the present invention is not limited to sequentially firing or even firing engines.

In accordance with the preferred embodiments of the present invention, a first level of furcation members, which are preferably bifurcation members, are associated with the ports of the cylinders in the manner described above, whereby for each pair of cylinders the flow path associated therewith branches from one primary passage into two secondary passages. The first level of furcation members are referred to as a first level because they are the furcation members that are fluidly closest to the cylinders. A first reduction in manifold passages is facilitated by employing the first level of bifurcation members. A single "pulse" interval is defined in each of the secondary passages due to the fluid communication with the cylinder associated directly therewith. A "pulse" corresponds to the rapid movement of a volume of air into a cylinder when that cylinder is temporarily fluidly communicating with an intake manifold. A "pulse" also corresponds to the rapid movement of a volume of air out of a cylinder when that cylinder is temporarily in fluid communication with an exhaust manifold. Pulεes can also be characterized in terms of acoustic events or pressure waves. A pulεe interval (pulse frequency) is defined as the interval (e.g., degrees of crankshaft revolution) between pulεeε.

For example and not limitation, a pulεe occurs in each of the εecondary paεsages of a firεt level bifurcation member every 720 degreeε and every 360 degreeε of crankεhaft rotation, respectively, for four- stroke engines, and every 360 and 180 degrees respectively for two-stroke engines. That is, a volume of gas is drawn into (or forced into) a representative intake port every 720 degrees and every 360 degrees of crankshaft rotation, respectively, for four-stroke engineε, and every 390 and 180 degreeε reεpectively for two-stroke engines. Similarly, a volume of gas is expelled from a representative exhaust port every 720 degrees and every 360 degrees of crankshaft rotation, reεpectively, for four-εtroke engines, and every 390 and 180 degrees respectively for two-stroke engines. The scope of the present invention is not limited to four-stroke and two-stroke engines. In accordance with the preferred embodiments of the preεent invention and in the case of even firing engines, the pulse interval of the primary passages of the first level bifurcation members is equal to half of the pulse intervals of the secondary passages of the first level bifurcation members. This relationship exists due to the fact that, in accordance with the preferred embodiments of the preεent invention, paired cylinderε are half way through the firing order from each other.

In accordance with the preferred embodiments of the present invention, a εecond level of furcation memberε are connected to and fluidly communicate with the primary passageε of the firεt level of furcation members. The second level of furcation members are referred to as a second level because they are the furcation members that are second closest (from a fluid communication standpoint) to the cylinderε. In accordance with a first preferred embodiment of the present invention, internal combustion engineε having at leaεt five cylinders are employed, and a second reduction in manifold paεsageε is facilitated by employing a second level trifurcation member or a εecond level of trifurcation members. For example and not limitation, when an engine is employed that has a number of cylinderε that iε equal to εix, the second reduction in passages is preferably facilitated with a single trifurcation member. For further example and not limitation, when an engine is employed that has a number of cylinders that iε equal to twelve, or other multiples of six, the second reduction in passageε is preferably facilitated with a plurality of trifurcation members, wherein the number of second level trifurcation members is equal to the number of cylinders divided by six. For example, a representative trifurcation member at the second level includes a primary passage that branches into three secondary passages. Each of the secondary passages of the trifurcation member at the second level individually connects to and communicates with a primary pasεage of a bifurcation member at the first level. In accordance with the firεt preferred embodiment of the present invention, the trifurcation member(s) is arranged such that the pulse interval of the primary passage of each second level trifurcation member is equal to one third of the pulse intervals of the primary passageε of the first level of furcation members. In accordance with a εecond preferred embodiment of the preεent invention, internal combuεtion engines having at least six cylinders are employed, and a εecond reduction in manifold passages is facilitated by employing a second level of bifurcation members. For example and not limitation, when an engine is employed that has a number of cylinders that iε equal to a power of 2, wherein the exponent is a whole number greater than 3 (e.g., when the number of cylinders is 8, or 16, or 32, or 64 . . .) the reduction in passages is preferably facilitated at the second level with a plurality of bifurcation members. For example, a representative bifurcation member at the second level includes a primary passage that branches into two secondary passages. Each of the secondary passages of the bifurcation member at the second level individually connects to and communicates with a primary pasεage of a bifurcation member at the first level. In accordance with the second preferred embodiment of the present invention, the εecond level of bifurcation members iε arranged εuch that the pulse interval of the primary pasεage of each second level bifurcation member is equal to half the pulse interval of the primary passages of the first level of furcation members.

In accordance with the first and second preferred embodimentε of the present invention, when an engine with more than six cylinders (or certain groups of engineε wherein the group haε a total of at least six cylinders) are employed, a third level furcation member or a third level of furcation members, or additional levels of furcation members are employed until a reduction to a εingle primary passage is achieved. For example, the additional levelε are referred to herein aε third, fourth, and fifth levels, etc., wherein each successive level is more distant, from a fluid communication standpoint, from the cylinders. It is most preferably for furcation members at the third and higher levels to be in the form of bifurcation members. Each of the higher level bifurcation members includes a primary passage that branches into two secondary paεεages. The secondary passages of each higher level bifurcation member attach to and are in fluid communication with the primary pasεage of a lower level furcation member. For each higher level bifurcation member employed, it iε preferable that the lower level primary passageε to which that higher level bifurcation member iε attached have identical, yet out of phaεe, pulse intervals. It is alεo preferable for the primary paεεage of each of the higher level bifurcation members to have a pulεe interval equal to half of the pulse intervals of its secondary passages. In accordance with a third preferred embodiment of the present invention, for internal combustion engines having an even number of cylinders greater that eight, but not the number of cylinders diεcussed above with reference to the first and second preferred embodiments, a second reduction in manifold passages is facilitated by a εingle second level multifurcation member having a primary passage that branches into more than three secondary passages. Most preferably the number of secondary passages of the multifurcation member is equal to an odd number greater than three. Each of the secondary pasεages of the multifurcation member individually connects to and communicateε with a primary paεsage of a bifurcation member at the first level. In accordance with the third preferred embodiment of the present invention, the second level multifurcation member is arranged such that the pulse interval of the primary pasεage thereof is equal to the pulse interval of the primary pasεageε of the first level bifurcation members divided by the number of first level bifurcation members. In summary, in accordance with the preferred embodiments of the preεent invention, intake and exhaust manifolds are provided which include a plurality of uniquely interconnected furcated pasεages. The furcated passageε are arranged in levels, and the number of furcated passages decrease in levels more fluidly distant from the engine associated therewith. The secondary pasεageε of a repreεentative furcation member preferably each have an identical, yet out of phase, pulεe interval εuch that the primary passage of that furcation member has a pulse interval equal to the pulse interval of the secondary pasεageε of the representative furcation member divided by the number of secondary passages of the representative furcation member. The arrangement of the furcated passages and the pulse interval relationship are such that substantially equal flow is established through the secondary passages of the first level furcation memberε. Thuε, at any given engine speed, all of the cylinders conεistently receive and expel an equal amount of inflow or outflow such that each of the cylinders react (e.g., fire) evenly and predictably.

In accordance with the preferred embodimentε of the preεent invention, each of the paεεageε defineε a cross-εectional area, wherein the croεε-sectional area of a passage can acceptably be measured perpendicular to the direction of flow through the most restrictive portion of the passage. In accordance with the preferred embodiments of the present invention, each successively encountered downstream passage in an intake manifold defines a smaller cross-sectional area. In accordance with the preferred embodiments of the present invention, each succesεively encountered downstream passage in an exhaust manifold defines a larger crosε-sectional area. In accordance with the preferred embodiments of the present invention, where a furcation member is connected to lower level furcation members, the secondary passages of the higher level furcation member are coextensive with the primary pasεageε of the lower level furcation members. That is, a higher level secondary passage and its coextensive lower level primary paεεage conεtitute a εingle passage.

In accordance with the preferred embodiments of the present invention, the uniquely interconnected furcated pasεageε and their pulse interval relationshipε function to greatly reduce pumping losses through the furcation members individually aε well as through groupε of furcation members. Stated differently, in accordance with the preferred embodiments of the present invention, pumping losses in manifolds are minimized due to the fact that the present invention converts detrimental inertia in manifolds into recovered productive inertia. Reduced pumping losεeε allow for successively greater crosε sectional areas to be employed in passageε in the furcation members, which increase in crosε-sectional area allows for lower velocities in those passages, which lower velocities result in a further reduction in pumping loses.

As a contraεting example, much detrimental inertia muεt be overcome in an internal combustion engine that includes a single elongated passage that functions as an exhaust manifold through which gasses pass with respect to a single cylinder. For example, a portion of the mechanical energy created by the engine must be εpent to push a pulse (i.e., volume of gas) from the cylinder and into the pasεage. Between pulses frictional forces tend to render conditions within the passage stagnant. Thus, not only must the engine expend mechanical energy to push a pulse from the cylinder, the engine must also expend mechanical energy to impart motion upon all of the gasεes that have become stagnant within the passage so that room iε made for the pulεe being discharged. In contrast, the passageε of the manifolds of the present invention are εtrategically paired to cylinders, and then repeatedly furcated in a manner that maintains the separation of initial secondary passageε and maximizes the pulse frequency (while maintaining a single pulse frequency) in subεequent secondary and primary pasεageε. It εhould be appreciated that aε a pulεe frequency in a paεsage increases (while a single pulse frequency is maintained) , the flow through that passages tends to become smooth and continuous. That is, periods of stagnation and movement do not alternate, whereby inertial pumping losses are minimized.

As an additional example of the flow enhancement of the present invention, in accordance with the preferred embodiments of the present invention, the furcated pasεages of intake manifolds and their pulse interval relationshipε function to employ the back- flow generated by one cylinder of a pair of cylinderε to aid in the filling of the other cylinder of the pair of cylinders. As stated previously, the paired cylinders are fired half way through the firing order from one another and breathe through a common bifurcation member. The utilization of back-flow is achieved, in part, by virtue of the fact that the paired cylinders are half way through the firing order from each other. Thus, for example and not limitation, aε the intake valve of the first cylinder of the pair of cylinders is closed, a gas rushing toward the first cylinder bounces backward off of the intake valve of the first cylinder. The gas that is bounced off of the intake valve of the first cylinder is directed, by virtue of the design of the first level bifurcation memberε, toward the intake valve of the second cylinder of the pair of cylinders, at which time the intake valve of the second cylinder is preparing to open or opened εuch that the gas bounced off of the intake valve of the first cylinder increases the pressure proximate to the second cylinder. That increased presεure enhanceε the flow into the εecond cylinder. Such utilization of back- flows enhances engine efficiency and power. While examples throughout this discloεure make reference to intake valveε and exhaust valves, those references to such valves are intended to be exemplary and are not to limit the scope of the present invention. The concepts explained with respect to intake and exhaust valves also apply to engines that do not incorporate such valves.

Further regarding intake manifolds, in accordance with the present invention the intake gas flow energy succesεively increases in preceding upstream pasεageε (i.e., the frequency εuccesεively decreases in εucceεεively encountered downstream passageε) by virtue of the fact that the pulεe frequency successively increases in precedingly encountered upstream passages which allows successively larger upstream cross- εectional areas to be utilized. Further the succesεive increase in pulse frequency increases the velocity of intake gasses in succeεεively encountered upstream passages, and the greater cross-sectional areas in the upstream pasεageε minimize flow resistance and thereby maintain flow energy within succeεεively encountered upεtream paεsages.

Aε a further example of the flow enhancement of the present invention, in a representative furcation member in an exhauεt manifold, flow through a first secondary paεεage of that furcation member into the primary paεsage of that furcation member draws gasεeε out of a second secondary passage of that furcation member. This decreaseε the preεεure proxmiate to the second cylinder prior to its valve opening, which decrease in pressure enhances the exhausting of the reεpective cylinder into its secondary passage. In similar fashion, flow through second and higher level furcation members draws gasses out of first level bifurcationε in a manner that further decreaεes the presεure in the firεt level furcations, which decrease in pressure enhances exhausting from the cylinders.

As another contrasting example, after a volume of exhaust gas iε discharged from a cylinder into certain manifolds, that volume of gas travels along an isolated paεεage away from the cylinder. Aε the volume of gas continues to travel, the traveling of the volume of gas tends to create a vacuum upstream from the volume of gas upon exhauεt valve cloεure, which vacuum tendε to cauεe the volume of gaε to detrimentally reverse its direction of flow and flow back upstream. Such reverεal of flow iε inefficient because the engine must expend energy to both exhaust the subsequent volume of gas and reverεe the flow of the prior volume of gaε such that both volumes of gas flow downstream. In accordance with the present invention, the fluid communication between primary and secondary passages in the first level and subεequent furcation members seekε to preclude such reversal of flow by increasing the forward flow energy of exhaust gases within successive downstream paεsages. This flow energy increaseε in each εucceεεively encountered paεεage. The flow energy is increased by virtue of the fact that the pulse frequency succesεively increases in successively encountered downstream passages which allows successively larger cross- sectional areas to be utilized. Further, the successive increase in pulse frequency tends to increase the velocity of exhaust gasεeε in successively encountered downstream passages, and the greater cross-sectional areas in the downstream passages seeks to minimize flow resistance and thereby maintain the flow energy within succesεively encountered downstream passages.

As a further example of the flow enhancement of the present invention, in accordance with the preferred embodiments of the present invention, the intake valves of paired cylinders are not open at the same time. Thus, in accordance with the preferred embodiments of the present invention, paired cylinders do not tend to compete among themselves for gas. Similarly, in accordance with the preferred embodiments of the preεent invention, the exhaust valveε of paired cylinderε are not open at the εame time. Thus, in accordance with the preferred embodiments of the preεent invention, paired cylinders do not tend to force exhaust gasses into one another or compete for a place to discharge gases. Of course the opening and closing of valves iε dependent upon the valve timing of an engine. However, by virtue of the fact that paired cylinders are preferably half way through the firing order from each other, in accordance with the preferred embodiments of the present invention it is posεible for valves to be open for an extended period of time while still precluding valve overlap (i.e., insuring that the intake valveε of paired cylinders are not open at the same time and that the exhaust valves of paired cylinders are not open at the same time). For example and not limitation, in a four stroke engine in which the valveε of each cylinder open in even frequency intervals meaning that the crankshaft rotates the same angular distance between each successive valve opening, the valves of paired cylinders can remain open for a maximum interval of up to but not including 360 degrees of crankshaft revolution while still precluding valve overlap. Alεo for example and not limitation, in a two stroke engine in which the valves of each cylinder open in even frequency intervals meaning that the crankεhaft rotates the same distance between each successive valve opening, the valves of paired cylinders can remain open for a maximum interval of up to but not including 180 degrees of crankshaft revolution while still precluding valve overlap. While examples throughout this disclosure make reference to intake valves and exhaust valves, those referenceε to εuch valves are intended to be exemplary and are not to limit the scope of the present invention. In other words, the concepts explained with respect to intake and exhaust valves alεo apply to engineε that do not incorporate such valves.

In accordance with certain embodiments of the present invention, paired cylinders (i.e., cylinderε that fire half way through the firing order from each other) are diεplaced from one another by virtue of the fact that one or more cylinderε are interpoεed between the paired cylinders. Such configurations are typical of conventional engines having more than two cylinders due to the fact that it has been conventional to place an emphasis on the balancing of engines. Alternatively, and in accordance with a fourth preferred embodiment of the present invention, paired cylinders are adjacent to one another. As a result of the adjacent configuration of paired cylinderε, in accordance with the fourth preferred embodiment of the preεent invention, the first level bifurcation members are centered with respect to their respective pair of cylinders and the lengths of the secondary passages are preferably minimized and equalized. By so minimizing and equalizing the lengths of pasεages, the benefits of the present invention discussed above are inventively enhanced. Similarly, in accordance with the forth preferred embodiment of the present invention, second and higher level furcationε are centered with respect to their respective lower level furcations such that the lengths of the secondary passages of second and higher level furcations are also minimized and equalized. In accordance with the fourth preferred embodiment of the present invention, the ability to minimize and equalize passage lengths seeks to enhance the tuning of the manifolds. Alεo, it iε preferable to counterbalance the engineε of the fourth preferred embodiment with weightε.

Interconnected groupε of engineε are also within the scope of the present invention. Thus, in accordance with certain embodiments of the present invention, references to an engine should also be conεidered to be a reference to a group of engineε. In accordance with the preferred embodiments of the present invention, engines within a group of engines are preferably configured such that all of the cylinders within the group of engines fire sequentially and also fire in an even frequency interval. This means that if the engines are operating at a constant speed, it is preferable that an equal amount of time paεεes between each successive cylinder firing. It is therefore an object of the present invention to enhance the operation of machines with multiple working chambers.

Another object of the preεent invention is to provide improved multi-cylinder machine breathing methodε, and apparatuε for implementing the improved methods.

Yet another object of the present invention is to enhance the operation of reciprocating pumps.

Still another object of the present invention is to provide improved breathing methods for internal combuεtion engines, and apparatus for implementing the improved methods.

Still another object of the present invention is to increase the energy efficiency of internal combustion engineε.

Still another object of the preεent invention is to provide more uniform combustion characteristics in internal combustion engineε.

Still another object of the present invention is to provide an improved combustion method for internal combustion engines, wherein the improved method εeekε to eεtabliεh equivalent breathing characteriεticε for each cylinder of a multi-cylinder internal combustion engine εuch that the compreεεion and expanεion eventε within the cylinderε are εubεtantially uniform and conεistent from one cycle to another.

Still another object of the present invention is to provide an improved combustion method for internal combustion engines, wherein the improved method seeks to establish equivalent breathing characteristics for each cylinder of a multi-cylinder internal combustion engine such that the pressure and heat associated with compression and expansion events within the cylinderε are εubstantially uniform and consistent from one cycle to another. Still another object of the present invention is to provide a method for combusting a combustible working fluid, wherein regular and predictable gaεeous communication causes the duration of compresεion and expanεion eventε to be equivalent from one cycle to another for a given engine operating εpeed when all other variableε remain constant.

Still another object of the present invention is to provide engines with reduced vibrationε due to smoother and more uniform combustion characteristics from one cycle to another.

Still another object of the present invention is to provide engines that are capable of including less mass by virtue of the fact that the engines have smoother and more uniform combustion characteristics. Still another object of the present invention is to increase the specific power output of internal combustion engines.

Still another object of the present invention is to decrease the fuel consumption of internal combustion engines.

Still another object of the present invention is to reduce the amount of pollutants exhausted from internal combustion engines.

Still another object of the present invention is to reduce the amount of pumping losεes associated with internal combustion engineε.

Still another object of the preεent invention iε to utilize back-flow within intake manifolds to charge cylinderε. Still another object of the preεent invention is to utilize back-flow within exhauεt manifolds to enhance the exhausting of cylinders.

Still another object of the preεent invention iε provide new manifoldε.

Still another object of the preεent invention iε to provide new engineε that optimize the effectiveneεs of the new manifolds.

Still another object of the present invention is to join multiple engines together with intake and/or exhaust manifoldε to synergistically enhance the breathing characteristics of the joined engines. BRIEF DESCRIPTION OF THE DRAWINGS

Othar objectε, featureε and advantageε of the present invention will become apparent upon reading and understanding this specification, taken in conjunction with the accompanying drawings:

Fig. 1 is a schematic flow diagram of a manifold and portions of an engine, in accordance with a first example of the first preferred embodiment of the present invention; Fig. 2 is a front perspective view of the manifold of Fig. 1 in the form of an intake manifold, in accordance with the first example of the first preferred embodiment of the present invention;

Figε. 3 and 4 are rear and side perspective views, respectively, of the manifold of Fig. 2;

Fig. 5 is a schematic flow diagram of a manifold and portions of an engine in accordance with a second example of the first preferred embodiment of the preεent invention; Fig. 6 iε a perεpective view of a manifold in accordance with a firεt example of the εecond preferred embodiment of the preεent invention;

Figε. 7-10 are top, right side, front end, and left side viewε, respectively, of the intake manifold of Fig. 6;

Fig. 11 is a cross-εectional view of the manifold of Fig. 6 taken along line 11-11 of Fig. 8;

Fig. 12 iε a schematic flow diagram of the manifold of Fig. 6 and portions of an engine, in accordance with the first example of the second preferred embodiment of the present invention;

Fig. 13 is a schematic flow diagram of a manifold and portionε of an engine in accordance with a firεt example of the third preferred embodiment of the preεent invention; Fig. 14 is a side perspective view of a manifold in accordance with a first example of the fourth preferred embodiment of the present invention;

Figs. 15-17 are top, front end, and rear end views, respectively, of the manifold of Fig. 14; Fig. 18 is a schematic flow diagram of the manifold of Fig. 14 and portions of an engine, in accordance with the first example of the fourth preferred embodiment of the preεent invention;

Figε. 19 and 20 are εide and front isolated, schematic, elevational viewε, reεpectively, of a crankshaft for the engine of Fig. 18;

Fig. 21 is a schematic flow diagram of a manifold and portions of an engine, in accordance with a first and second example of the fourth preferred embodiment of the present invention;

Figε. 22 and 23 are εide and front isolated, schematic, elevational views, respectively, of a crankshaft for the engine of Fig. 21, in accordance with the first example of the fourth preferred embodiment of the present invention;

Fig. 24 is a schematic flow diagram of four engines that are connected by manifolds, in accordance with a fourth example of the fourth preferred embodiment of the present invention; Figs. 25-28 are schematic flow diagramε of manifoldε and portions of engines in accordance with other example of the fourth preferred embodiment of the present invention; and,

Figε. 29-36 are εchematic flow diagrams of the manifold and engine of Fig. 21, wherein relative pressures and flows are depicted;

DETAILED DESCRIPTION OF THE EMBODIMENTS

Referring now in greater detail to the drawingε, in which like numeralε represent like components throughout the several views, Fig. 1 is a schematic flow diagram of a manifold 20 and portionε of a conventional, in-line six cylinder, reciprocating, internal combustion engine 22, in accordance with a first example of a first preferred embodiment of the present invention. Throughout this disclosure, all references to cylinders should be considered to be references to working chambers, as the preεent invention is not limited to working chambers that are in the shape of cylinders. The engine 22 includeε cylinderε 1-6. Throughout the figureε of thiε diεcloεure, cylinder numbers are proceeded by the letter "C". The engine 22 has a conventional firing order of 1-5-3-6-2-4. The cylinders 1-6 include ports 24a-f, respectively. The cylinders 1-6 also acceptably includeε valveε 26a-f, respectively. The valves 26a-f are εchematically repreεented by "X"ε. In accordance with the embodiment depicted in Fig. 1, the valveε 26a- f open and cloεe to provide and preclude, reεpectively, communication between the cylinderε 1-6 and their respective ports 24a-f in a conventional manner, as should be understood by those reaεonably skilled in the art. It is acceptable for all of the engines of the embodiments of the present invention to include valves (both intake and exhaust) that are similar to the valves 26a-f. It is also acceptable for all of the engineε of the embodiments of the present invention to include portε (both intake and exhauεt) that are εimilar to the portε 24a-f. Such valveε and portε are not expressly included in the majority of this disclosure because such valves and ports should be understood by those reasonably skilled in the art.

5 The preεent invention alεo expreεεly applies to machines with cylinderε that do not εpecifically include such valves and ports.

The manifold 20 includes a first level of bifurcation members 28a-c. Each bifurcation member

1028a-c includes a primary pasεage 34 that brancheε into a pair of εecondary passages 30,32. The secondary pasεageε 30,32 of each first level bifurcation member 28 are individually in fluid communication with the ports 24 of a pair of cylinders that fire half way

15 through the firing order from each other. The manifold 20 further includes a second level trifurcation member 36 that includes a primary passage 44 that branches into three secondary paεεageε 38,40,42. The primary paεεageε 34 of each of the first level bifurcation

20 members 28 are individually in fluid communication with one of the secondary pasεageε 38,40,42 of the εecond level trifurcation member 36. In accordance with the preferred embodimentε of the preεent invention, each primary passage of a first level furcation member (for

25 example see the primary paεεage 34a of the firεt level bifurcation member 28a) coextends with (i.e., is the same pasεage as) a secondary paεsage of a second level trifurcation member (for example see the secondary passage 38 of the second level trifurcation member 36).

30 In the schematic flow diagram of Fig. 1, the passageε 30,32,34,38,40,42,44 are represented as lines. Similar passages are also repreεented with lineε in the other schematic flow diagrams of this disclosure. Throughout this diεcloεure, the passages represented as

35 lines are identified with broken lines that lead from identifying numerals. Further, it should be understood that the εchematic flow diagrams of this disclosure are intended to identify which pasεageε are in fluid communication; connected paεεages are in fluid communication. The u-shapeε in the εchematic flow diagramε that are positioned at the croεεing of two paεsages repreεent that the crossing pasεages do not directly connect or fluidly communicate. For example, in Fig. 1, the passage 34b,40 includes two such u- shapes (i.e., the pasεage 34b,40 does not directly connect to or communicate with the passages 30c,32a) and the pasεage 34c,42 includeε one such u-shape (i.e., the passage 34c,42 does not directly connect to or communicate with the passage 32a). Further, the schematic flow diagrams of this disclosure are not intended to show spatial relationships of passageε.

Throughout this discloεure, manifoldε that are depicted in schematic flow diagram form represent both intake and exhaust manifolds, unless specified specifically or implicitly otherwise. In accordance with the first example of the firεt preferred embodiment of the preεent invention, that which iε depicted in Fig. 1 is representative of both an intake manifold and an exhaust manifold. That is, in one embodiment the manifold 20 iε representative of an intake manifold, the valves 26 are representative of intake valves, and the ports 24 are representative of intake ports. Similarly, in another embodiment the manifold 20 iε repreεentative of an exhauεt manifold, the valves 26 are representative of exhauεt valves, and the ports 24 are representative of exhaust ports.

I accordance with the first example of the first preferred embodiment of the preεent invention, the engine 22 iε a four stroke engine, wherein the cylinders are evenly fired in sequence at intervals which are 120 degrees of crankshaft revolution apart. Accordingly, the cylinders each breathe (i.e., pulse) in sequence at intervals which are initiated 120 degrees of crankshaft revolution apart. In accordance with the preferred embodiments of the present invention, and referring to intake manifolds, a "pulse" corresponds to the rapid movement of a volume of air into a cylinder from the intake manifold, which rapid movement typically has aεsociated therewith an acoustic event or events and pressure waves. In accordance with the preferred embodiments of the present invention, and referring to exhauεt manifoldε, a "pulse" correspondε to the rapid movement of a volume of air out of a cylinder and into the exhaust manifold, which rapid movement typically has associated therewith an acoustic event or events and pressure waves. In accordance with the preferred embodiments of the present invention, only one cylinder pulses with respect to a first level bifurcation member 28 at a time. In accordance with the first example of the first preferred embodiment of the present invention, each of the valves 26 opens sequentially and remains open for a duration such as, but not limited to, 300 degrees of crankshaft revolution, and the two valves which share a common first level bifurcation member 28 are not open to that bifurcation member 28 at the same time. In accordance with the first example of the first preferred embodiment, each of the εecondary passages 30,32 of each first level bifurcation member 28 has a pulse interval of 720 degrees of crankshaft revolution. The pulse interval of the secondary passages 30,32 of each first level bifurcation member 28 are phased 360 degrees of crankshaft revolution apart (e.g., the pulεe frequency of the εecondary passage 30a is 360 degrees of crankshaft revolution out of phase from the pulse frequency of the εecondary passage 32a). The primary passage 34 of each of the first level bifurcation members 28 has a pulse interval of 360 degrees of crankεhaft revolution. The pulse intervals of the primary passages 34 of the first level bifurcation members 28 are phased 120 degrees of crankshaft revolution apart. The pulεe interval of the primary passage 44 of the second level trifurcation member 36 iε 120 degrees of crankshaft revolution.

Figs. 2-4 are front, rear, and side perspective views of the manifold 20 in the form of an intake manifold, in accordance with the first example of the first preferred embodiment of the present invention. In Figs. 2-4, the paεεageε identified in Fig. 1 are generally not εeen. In the embodiment of Figε. 2-4, the passages identified in Fig. 1 are defined within tubes, which tubeε are identified by the numerals of their corresponding passages. The primary passage 44 of the second level trifurcation member 36 defines an inlet opening 45 (Fig. 2) to the manifold 20. The manifold further includes a base plate 46. Each of the tubes that define the secondary pasεageε 30a- c,32a-c are connected to and extend from the baεe plate 46. The base plate 46 defines outlet passages 48a-f therethrough that are in fluid communication with the pasεageε 30a-c,32a-c, reεpectively. Further, the base plate 46 preferably defines a plurality of bolt holes therethrough which facilitate the bolting of the manifold to the engine 22 (Fig. 1). In an alternate embodiment of the preεent invention, the manifold 20 depicted in Figε. 2-4 iε preferably reconfigured such that all of the components of the second level trifurcation member 36 εlope upward and forward from the other components of the manifold 20 such that the manifold defines a more compact profile.

As depicted in Figε. 2-4, it iε preferable in all of the preferred embodiments of the present invention for each of the firεt level bifurcation members (such aε firεt level bifurcation memberε 28a-c) to be constructed and arranged to be T-shaped. The T-shape iε εuch that, where paired secondary passageε (such as secondary passages 30a,32a) join, the centerlines of the joining secondary pasεageε are collinear such that

5 back-flow between the paired secondary passages is enhanced, aε discussed in greater detail below. As depicted for example in Figs. 2-4, in accordance with the preferred embodimentε of the present invention, where a furcation member is connected to lower level

10 furcation members, the secondary passageε of the higher level furcation member are coextensive with the primary passages of the lower level furcation members. Alternatively bifurcation memberε (such as first level bifurcation members 28a-c) are constructed and arranged

15 to be Y-shaped.

In accordance with the example of the first preferred embodiment of the present invention depicted if Figε. 2-4, the bifurcation memberε 28 and trifurcation member 36 are acceptably constructed of 16

20 gauge mild steel round tubing. For example and not limitation, the manifold depicted in Figs. 2-4 is acceptably constructed and arranged such that the outer diameters and lengths of all of the secondary passages 30,32 of the first level bifurcation members 28 are

253.00 inches and 43.5 incheε, reεpectively; the outer diameterε and lengths of all of the primary passageε 34 of the firεt level bifurcation members 28 are 3.25 inches and 25.5 inches, respectively; and the outer diameter and length of the primary pasεage 44 of the

30 second level trifurcation member 36 are 4.00 inches and iε 6.0 inches, respectively. The manifold depicted in Figs. 2-4 is acceptably used in place of the stock intake manifold on a 12.7 liter, turbocharged, in-line six cylinder, diesel engine. An acceptable example of

35 such engine is available from the Detroit Diesel Corporation which is located in Detroit Michigan. Fig. 5 is a schematic flow diagram of a manifold 50 and portions of a V-type twelve cylinder, reciprocating, internal combustion engine 52, in accordance with a second example of the first preferred embodiment of the present invention. The engine 22 includes cylinders 1-12 and has a firing order of 1-7-6-12-5-11-4-10-3-9-2-8. The manifold 50 includes a first level of bifurcation members 54a-f. Each of the first level bifurcation memberε 54a-f includeε a primary paεεage 60 that branches into a pair of secondary paεεageε 56,58. The secondary pasεageε 56,58 of each firεt level bifurcation member 54 are individually in fluid communication with a cylinder of a pair of cylinders that fire half way through the firing order from each other. The manifold 50 further includes εecond level trifurcation members 62a,b. Each of the second level trifurcation members 62 includeε a primary paεεage 70 that branches into secondary passageε 64,66,68. The primary paεεageε 60 of each of the first level bifurcation members 54 are individually in fluid communication with and coextensive with the secondary paεεageε 64,66,68 of the second level trifurcation members 62. In accordance with the second example of the first preferred embodiment, the manifold 50 further includeε a third level bifurcation member 72 that includes a primary passage 78 that branches into a pair of secondary paεsages 74,76. The primary passages 70 of each of the second level trifurcation members 62 are individually in fluid communication with and coextensive with the secondary paεεageε 74,76 of the third level bifurcation member 72.

In accordance with the εecond example of the first preferred embodiment of the present invention, the engine 52 is a four stroke engine, wherein the cylinders are fired in sequence at intervals which are 60 degrees of crankshaft revolution apart. Accordingly, the cylinderε each breathe (i.e., pulse) in sequence at intervals which are initiated 60 degrees of crankshaft revolution apart. In accordance with the second example of the first preferred embodiment, each of the secondary paεsages 56,58 of each first level bifurcation member 54 has a pulse interval of 720 degrees of crankshaft revolution. The pulse interval of the secondary passages 56,58 of each first level bifurcation member are phased 360 degrees of crankshaft revolution apart. The primary paεsage 60 of each of the firεt level bifurcation members 54 has a pulse interval of 360 degrees of crankshaft revolution. The pulεe intervalε of the primary passages 60 of the first level bifurcation members 54 are phased 120 degrees of crankεhaft revolution apart. The pulse interval of the primary passages 70 of the second level trifurcation members 62 are 120 degrees of crankshaft revolution. The pulse intervals of the primary passageε 70 of the εecond level trifurcation members 62 are phased 60 degrees of crankshaft revolution apart. The pulse interval of the primary passage 78 of the third level bifurcation member 72 is 60 degrees of crankshaft revolution.

Aε mentioned above, the schematic flow diagrams of this disclosure are generally not intended to show spatial relationshipε of paεεages. Notwithstanding, in accordance with the preferred embodiments of the preεent invention, where V-type engines are employed, it is often preferable for a majority of the intake manifolds of the preεent invention to be εubstantially εituated between the cylinder banks of the V-type engine, whereby the manifold 50 depicted in Fig. 5 is at least somewhat spatially representative of an intake manifold. Alternatively, where V-type engineε are employed, it iε often preferable for a majority of the exhauεt manifoldε of the present invention to not be substantially εituated between the cylinder bankε of the V-type engine.

In accordance with a third example of the firεt preferred embodiment of the present invention, the engine 52 of Fig. 5 can be conεidered to be two different engines that are connected by the manifold 50. In accordance with the third example of the first preferred embodiment of the present, cylinders 1-6 depicted in Fig. 5 co priεe a firεt V-6, four stroke engine 80 having a firing order of 1-6-5-4-3-2, and cylinders c7-cl2 comprise a second V-6, four stroke engine 82 having a firing order of 7-12-11-10-9-8. In accordance with the third example of the first preferred embodiment, the engine 80 is preferably εelf contained such that it contains all of the necessary components to operate irrespective of the operation of the engine 82. Similarly, the engine 82 is preferably self contained such that it contains all of the necesεary componentε to operate irreεpective of the operation of the engine 80 (i.e., the engine 80 haε a crankshaft that it separate from the crankshaft of the engine 82, etc.). However, in accordance with the third example of the first preferred embodiment of the present invention, the engines 80,82 are preferably fluidly interconnected by the manifold 50 in the manner depicted in Fig. 5, and the engines 80,82 are preferably phased 60 degrees of crankshaft revolution apart so that all of the pulse intervalε diεcuεsed above for the manifold 50 when installed on the V-12, four stroke engine 52 are representative of the pulεe intervalε when the manifold 50 iε connected to the pair of V-6 engines 80,82.

Fig. 6 is a perspective view of a manifold 110 in accordance with a first example of a second preferred embodiment of the present invention. The manifold 110 is pictorially depicted in the form of an intake manifold in Figs. 6-11, while the manifold 110 is repreεjanted in εchematic form in Fig. 12. Aε discusεed below with reference to Fig. 12, it should be understood that the flow-paths defined by the manifold 110 are, in accordance with the second preferred embodiment of the present invention, capable of being arranged to define both an intake manifold as well as an exhaust manifold. For explanatory purposes the present invention is in some cases explained in termε of @furcations@, however, the present invention is not to be limited by the usage of the term "furcationε". For example, Figs. 6-11 are explained in alternate terms that are capable of being applied throughout this disclosure. And for contrast, Fig. 12 is subsequently explained in terms of §furcations§. Thuε, it might be deεirable in an initial reading of thiε diεclosure to skip over the discusεion of Figε. 6-11.

Figε. 7-10 are top, right side, front end, and left side views, reεpectively, of the intake manifold 110 of Fig. 6. Fig. 11 is a cross-sectional view of the manifold 110 taken along line 11-11 of Fig. 8. As illustrated in Figs. 6-11, the manifold 10 is capable of being mounted on a typical V-8 engine block εuch aε the small block Chevrolet engine. The small block Chevrolet engine is used for illustrative purposeε only and εlight modifications of the manifold 110 will allow it to be used on other V-8 engineε. The manifold 110 includeε an air intake εection ill. The manifold 110 is mounted between the cylinder banks of the V-8 engine, and the manifold 110 is constructed and arranged so that the diεtance which fluid muεt travel from the air intake εection 111 to each of the cylinderε iε approximately the εame for all of the cylinderε. Referring to Fig. 7, the manifold 110 haε the following major componentε: the air intake εection 111, transfer εectionε 112, 113, distribution sections 114, 115, 116, 117, and intake port extensions 121, 126, 134, 137, 142, 143, 145, 148. The manifold 10 also includeε proviεionε for the installation of fuel injectors which can be located in mounting holeε 151, 152, 153, 154, 155, 156, 157, and 158. The air intake εection 111 iε fluidly connected to tranεfer sections

112, 113 which in turn are fluidly connected to distribution εections 114 and 115; 116 and 117, respectively. Distribution sectionε 114, 115, 116, 117 are themεelveε fluidly connected to intake port extenεionε 134 and 137; 121 and 126; 142 and 143; 145 and 148 respectively. The intake valve chambers of the engine are fluidly connected to the distribution sections by the intake port extensions 121, 126 protruding from the lower layer 120 of the tri-layered εtructure, extensions 134, 137 protruding from its middle layer 130 and extenεionε 142, 143, 145, 148 protruding from its upper layer 140. As mentioned above, in a typical application, manifold 110 is utilized on a small block Chevrolet V- 8 engine. The Chevrolet V-8 engine is arranged in two bankε of cylinderε, right and left, looking from the front of the vehicle. The cylinderε of thiε engine number from the front with the front right cylinder being cylinder 1, the front left 2, the εecond-fro - the-front right 3, the second-from-the-front left 4, the third-fro -the-front right 5, the third-from-the- front left 6, the fourth-from-the-front right 7, and the fourth-from-the-front left 8. The ignition firing order for this V-8 engine iε 1-8-4-3-6-5-7-2, and the cylinderε are fired in εequence at intervals which are 90 degrees of crankshaft revolution apart.

With this V-8 engine, the manifold 110 is arranged so that the diεtribution section 115 located in the lower layer 120 supplieε cylinderε 1 and 6 through air intake port extensionε 121 and 126, reεpectively. Distribution section 114 located in the middle layer 130 supplies cylinders 4 and 7 through air intake port extensions 134 and 137, respectively. Distribution εectionε 116, 117 in the upper layer 140 εupply cylinders 2 and 3; 5 and 8, respectively, through air intake port extensionε 142 and 143; 145 and 148, respectively.

As indicated by the firing order, ignition of cylinder 6 is separated from the ignition of cylinder 1 by an interval correεponding to 360 degreeε of crankshaft revolution. Similarly, cylinders 8 and 5, cylinders 4 and 7, cylinders 3 and 2 are ignited at time intervals which are separated by 360 degrees of crankshaft revolution. Therefore, the sharing of the same diεtribution εection 115, 117, 114, 116 by pairε of cylinders 1 and 6, 8 and 5, 4 and 7, 3 and 2, respectively, has no adverse effect on the opening of the intake valve of either cylinder in each of these pairs.

Moreover, after the intake valve for cylinder 1 opens, cylinder 8, the next cylinder to receive intake flow, is fed through the distribution εection 117 in the upper layer 140 by air intake port extension 148. Extension 148 is spatially εeparated from extension 121, which has just fed cylinder 1, by four distinguishable fluid flow channels defined by transfer sections 112 and 113 and by diεtribution εections 115 and 117. Hence, manifold 10 provides good separation between the intake flow for cylinder 8 and the pressure pulse created by the closing of the intake valve of cylinder 1.

Similarly, cylinder 4, the next cylinder to receive intake flow after cylinder 8, iε fed through the diεtribution section 114 in the middle layer 130 by air intake port extension 134. Extension 134 is spatially εeparated from extenεion 148, which haε juεt fed cylinder 8, by four diεtinguiεhable fluid flow channels defined by transfer sectionε 112 and 113 and by distribution sections 114 and 117.

5 Likewise, cylinder 3, the next cylinder to receive intake flow after cylinder 4, is fed through the distribution section 116 in the upper layer 140 by air intake port extension 143. Extension 143 iε spatially separated from extenεion 134, which haε juεt fed

10 cylinder 4, by four distinguishable fluid flow channels defined by transfer sections 112 and 113 and by distribution sections 114 and 116.

After cylinder 3, cylinder 6, the next cylinder to receive intake flow, is fed through the distribution

15 section 115 in the lower layer 120 by air intake port extenεion 126. Extenεion 126 iε spatially separated from extension 143, which haε juεt fed cylinder 3, by four distinguishable fluid flow channels defined by transfer sections 112 and 113 and by distribution

20 εectionε 115 and 116.

Next after cylinder 6, cylinder 5 receiveε intake flow fed through the diεtribution section 117 in the upper layer 140 by air intake port extension 145. Extension 145 is spatially separated from extension

25126, which haε juεt fed cylinder 16, by four distinguiεhable fluid flow channelε defined by tranεfer εections 112 and 113 and by diεtribution sections 115 and 117.

Immediately following cylinder 5, cylinder 7 is the

30 next cylinder to receive intake flow; and it is fed through the distribution section 114 in the middle layer 130 by air intake port extension 137. Extension 137 is spatially separated from extension 145, which has just fed cylinder 5, by four diεtinguishable fluid

35 flow channels defined by transfer sections 112 and 113 and by diεtribution sections 114 and 117. After cylinder 7, cylinder 2, the next cylinder to receive intake flow, iε fed through the diεtribution section 116 in the upper layer 140 by air intake port extension 142. Extenεion 142 iε εpatially separated

5 from extension 137, which has just fed cylinder 7, by four distinguishable fluid flow channels defined by tranεfer εectionε 112 and 113 and by diεtribution sections 114 and 116.

The next cylinder to fire again is cylinder 1

10 restarting the firing sequence. Cylinder 1 is fed through distribution section 115 in the lower layer 120 by extenεionε 121 which is spatially separated from extension 142 by four distinguishable fluid flow channels defined by tranεfer εectionε 112 and 113 and

15by distribution sections 115 and 116.

For each of the cylinders 8, 4, 3, 6, 5, 7, 2, 1, the manifold 110 provides good separation between the intake flow for each individual cylinder and the pressure pulse created by the closing of the intake

20 valve of cylinder 1, 8, 4, 3, 5, 6, 7, 2, respectively. The manifold 110 and conventional V-8 engine 108 are depicted in the form a εchematic flow diagram in Fig. 12, in accordance with the firεt example of the εecond alternate embodiment of the preεent invention. As

25 mentioned above, the manifold 110 is capable of being described in terms of furcations, and accordingly Fig. 12 is described in εuch termε. Also, in accordance with the first example of the second preferred embodiment of the present invention, the flow-paths

30 identified in Fig. 12 are representative of both intake and exhaust manifoldε. Aε mentioned above, the engine 108 haε a conventional firing order of 1-8-4-3-6-5-7-2. The manifold 110 includeε a firεt level of bifurcation members 160a-d. Each first level bifurcation member

35160a-d includes a primary paεsage 168 that branches into a pair of secondary passageε 162,164. The manifold 110 further includes second level bifurcation members 170a-b. Each of the second level bifurcation members 170 includes a primary passage 176 that branches into secondary pasεages 172,174. In accordance with the first example of the second preferred embodiment, the manifold 110 further includes a third level bifurcation member 178 that includes a primary passage 184 that branches into a pair of secondary passages 180,182. In accordance with the firεt example of the second preferred embodiment of the present invention, the engine 108 is a four stroke engine, wherein the cylinders are evenly fired in εequence at intervalε which are 90 degrees of crankshaft revolution apart. Accordingly, the cylinderε each pulse in sequence at intervals which are initiated 90 degrees of crankshaft revolution apart. In accordance with the first example of the second preferred embodiment, each of the εecondary passages 162,164 of each first level bifurcation member 160 haε a pulse interval of 720 degrees of crankshaft revolution. The pulεe intervalε of the secondary passages 162,164 of the first level bifurcation members 160 are phased 360 degreeε of crankshaft revolution apart. The primary paεεage 168 of each of the first level bifurcation members 160 haε a pulεe interval of 360 degrees of crankshaft revolution. The pulse intervals of the primary passageε 168 of the first level bifurcation memberε 160 are phased 180 degrees of crankshaft revolution apart. The pulse interval of the primary pasεageε 176 of the εecond level bifurcation memberε 170 iε 180 degreeε of crankεhaft revolution. The pulεe intervalε of the primary paεεageε 176 of the εecond level bifurcation members 170 are phased 90 degrees of crankshaft revolution apart. The pulse interval of the primary pasεage 184 of the third level bifurcation member 178 iε 90 degrees of crankshaft revolution.

Fig. 13 is a schematic flow diagram of a manifold 190 and portions of a V-10 engine 191 in accordance with a first example of a third preferred embodiment of the present invention. In accordance with the first example of the third embodiment, the engine 191 haε a firing order such as 1-10-4-7-6-2-9-3-8-5. The manifold 190 includes first level of bifurcation members 192a-e. Each of the first level bifurcation members 192 includes a primary passage 195 that branches into a pair of secondary passages 193,194. The secondary passages 193,194 of each of the first level bifurcation memberε 192 are for communicating with a pair of cylinders that are half way through the firing order from each other. The manifold 190 further includes a second level multifurcation member 196 that includeε a primary pasεage 198 that brancheε into a plurality of secondary passages 197a-e.

In accordance with the first example of the third preferred embodiment of the present invention, the engine 191 is a four stroke engine, wherein the cylinders are fired in sequence at intervalε which are 72 degreeε of crankshaft revolution apart. Accordingly, the cylinders each pulse in sequence at intervals which are initiated 72 degreeε of crankεhaft revolution apart. In accordance with the firεt example of the third preferred embodiment, each of the secondary passages 193,194 of the first level bifurcation members 192 have a pulse interval of 720 degrees of crankshaft revolution. The pulse intervals of the secondary pasεageε 193,194 of each of the first level bifurcation members 192 are phased 360 degrees of crankshaft revolution apart. The primary passages 195 of the first level bifurcation members 192 have pulse intervals of 360 degreeε of crankεhaft revolution. The primary pasεageε 195 of the first level bifurcation memberε 192 are phaεed 72 degrees of crankshaft revolution apart. The pulse interval of the primary paεεage 198 of the second level multifurcation member 196 is 72 degreeε of crankshaft revolution. Fig. 14 is a side perspective view of a manifold 200 in accordance with a first example of a fourth preferred embodiment of the present invention. The manifold 200 is depicted in the form of an intake manifold in Figs. 14-17, while the manifold 200 iε represented in εchematic form in Fig. 18. Aε diεcussed below with reference to Fig. 18, it should be understood that the flow-paths defined by the manifold 110 are, in accordance with the fourth preferred embodiment of the present invention, capable of being arranged to define both an intake manifold as well as an exhaust manifold. For explanatory purposes the present invention is in some cases explained in terms of @furcationε@, however, the preεent invention iε not to be limited by the uεage of the term "furcationε". For example, Figε. 14-17 are explained in alternate termε. And for contrast. Fig. 18 is subεequently explained in terms of @furcations@. Thus, it might be desirable in an initial reading of this disclosure to skip over the discusεion of Figε. 14-17. Figε. 15-17 are top, front end, and rear end viewε, reεpectively, of the manifold 200, in accordance with the first example of the fourth embodiment of the present invention. The manifold 200, as illustrated in the Figε. 14-17, iε designed for use with an eight- cylinder V-8 engine 202 (Fig. 18) wherein cylinders that are half way through the firing order from each other are adjacent. In accordance with the first example of the fourth embodiment of the present invention, the engine 202 has a firing order of 1-6-5-2-3-8-7-4.

Referring to Fig. 15, the manifold 200 can be characterized generally as comprising seven Ys and has the following major components: an air inlet section 211; transfer sections 212, 213; distribution sections 221, 222, 223, 224; and air intake port extensions 231,

5 232, 233, 234, 235, 236, 237, 238. The air inlet section 211 is fluidly connected to the transfer sectionε 212 and 213 through a Y. The transfer section 212 is fluidly connected to the distribution εections 221 and 222 through a Y 225, and the transfer section

10213 is fluidly connected to the distribution εectionε 223 and 224 through a Y 226. The peripheries of transverεe croεε-εections of fluid flow channels formed by the distribution sections 221, 222, 223, 224, are generally circular in shape. Each distribution section

15221, 222, 223, 224 is split into two intake port extensions by flow dividers. As shown in Fig. 14, distribution sections 221 and 222 are split into extensions 231, 232; 233, 234, respectively, by flow dividers 241, 242, respectively. Each of the intake

20 port extensions also has a port 251, 252, 253, 254, 255, 256, 257, 258, for mounting fuel injectorε (not shown) when they are utilized in the engine.

The manifold 200 performs for four-εtoke, V-8 engine as follows: A pulse of air or of fuel/air mixture for

25 engine charge enters the air inlet section 211 at opening 210 every 90 degrees of crankshaft revolution. Downstream of the section 211, the pulse is diverted into one of two transfer sectionε 212, 213, each of these transfer sectionε receiving εuch a pulεe each 180

30 degrees of crankεhaft revolution. Further downεtream, the diεtribution sections 221, 222, 223, 224 each receive such a pulse of air every 360 degreeε of crankεhaft revolution, and the air intake port extenεions 231, 232, 233, 234, 235, 236, 237, 238 each

35 receive such a pulse every 720 degrees of crankεhaft revolution. The manifold 200 and V-8 engine 202 are depicted in the form of a schematic flow diagram in Fig. 18, in accordance with the first example of the fourth preferred embodiment of the preεent invention. Aε mentioned above, the manifold 200 iε capable of being deεcribed in termε of furcations, and accordingly, Fig. 18 is described in εuch terms. Aε mentioned above, the engine 202 haε a firing order of 1-6-5-2-3- 8-7-4. The manifold 200 can be deεcribed aε including first level bifurcation members 260a-d. Each first level bifurcation member 260a-d includes a primary passage 266 that branches into a pair of secondary paεεageε 262,264. The manifold 110 can be further deεcribed as including second level bifurcation members 268a-b. Each of the second level bifurcation members 268 include a primary paεεage 274 that brancheε into a pair of εecondary paεεages 270,272. In accordance with the firεt example of the fourth preferred embodiment, the manifold 200 further includes a third level bifurcation member 276 that includes a primary pasεage 282 that brancheε into a pair of secondary passages 278,280.

In accordance with the first example of the fourth preferred embodiment of the present invention, the engine 202 is a four stroke engine, wherein the cylinders are fired in sequence at intervals which are 90 degrees of crankshaft revolution apart. Accordingly, the cylinders each pulse in sequence at intervals which are initiated 90 degrees of crankshaft revolution apart. In accordance with the first example of the fourth preferred embodiment, each of the secondary pasεages 262,264 of the first level bifurcation members 260 has a pulse interval of 720 degrees of crankεhaft revolution. The pulεe intervals of the εecondary paεsages 262,264 of the first level bifurcation memberε 260 are phased 360 degrees of crankshaft revolution apart. The primary passageε 266 of the firεt level bifurcation members 260 have pulse intervalε of 360 degrees of crankshaft revolution. The pulse intervalε of the primary pasεageε 266 of the firεt level bifurcation memberε 260 are phaεed 180

5 degreeε of crankshaft revolution apart. The pulse intervals of the primary paεsages 274 of the second level bifurcation members 268 are 180 degrees of crankshaft revolution. The pulse intervals of the primary paεsages 274 of the second level bifurcation

10members 268 are phased 90 degrees of crankshaft revolution apart. The pulse interval of the primary paεsage 282 of the third level bifurcation member 276 is 90 degreeε of crankεhaft revolution.

Fig. 19 iε an isolated, schematic, side elevational

15view and Fig. 20 is an isolated, schematic, front elevational view of a crankshaft 290 for the engine 202, in accordance with the first example of the fourth preferred embodiment of the present invention. The crankshaft 290 is constructed and arranged to

20 facilitate the firing order of 1-6-5- 2-3-8-7-4. The crankshaft 290 includes main bearing journals 292a-e that are connected to rod bearing journalε 294a-d by crank-arms 296a-h. The rod bearing journals 294a,b are preferably out of phase from the rod bearing journals

25294c,d by the angle "a" (Fig. 20) that is preferably 180 degrees of crankεhaft revolution. First and second connecting rods (not shown) are respectively connected between the rod bearing journal 294a and a first piεton (not εhown) diεpoεed within the first cylinder (Fig.

3018) and a second piston (not shown) dispoεed within the εecond cylinder (Fig. 18). The third and fourth cylinderε (Fig. 18) are similarly associated by way of connecting rods with the rod bearing journal 294b, the fifth and sixth cylinders (Fig. 18) are similarly

35 aεεociated by way of connecting rods with the rod bearing journal 294c, and the seventh and eighth cylinders (Fig. 18) are similarly associated by way of connecting rods with the rod bearing journal 294d. When oriented aε depicted in fig. 20, the crankshaft 290 preferably rotates clockwise.

5 Fig. 21 is a schematic flow diagram of a manifold 300, and an in-line, four cylinder engine 302 wherein paired cylinders are adjacent, in accordance with two additional examples of the fourth preferred embodiment of the present invention. In accordance with thoεe two

10examples of the fourth preferred embodiment, the engine 302 has a firing order of 1-3-2-4. The manifold 300 includes first level bifurcations members 304a,b. Each first level bifurcation member 304 includes a primary passage 310 that branches into secondary passageε

15306,308. The manifold further includes a second level bifurcation member 312 that includes a primary paεεage 318 that brancheε into εecondary paεεageε 314,316 .

In accordance with a εecond example of the fourth preferred embodiment, the engine 302 iε a four stroke

20engine such that the cylinderε each pulse in sequence at intervals which are 180 degrees of crankshaft revolution apart. Each of the εecondary paεsages 306,308 of the first level bifurcation members 304 have a pulse interval of 720 degrees of crankshaft

25 revolution. The pulse intervals of the secondary pasεages 306,308 of the first level bifurcation members 304 are phased 360 degreeε of crankεhaft revolution apart. The primary paεsages 310 of the firεt level bifurcation memberε 304 have a pulse interval of 360

30 degrees of crankshaft revolution. The primary pasεages 310 of the first level bifurcation members 304 are phased 180 degrees of crankshaft revolution apart. The pulse interval of the primary pasεage 318 of the εecond level bifurcation member 312 is 180 degrees of

35 crankshaft revolution. In accordance with a third example of the fourth preferred embodiment of the preεent invention, the engine 302 is a two stroke engine, wherein the engine 302 and manifold 300 cooperate to define pulse intervals that are related to those defined immediately above. Each of the pulse intervals identified immediately above is divided by two to calculate the pulεe intervalε associated with that two stroke engine.

In accordance with the second example of the fourth embodiment, the engine 302 includes a four stroke crankshaft 320 that is constructed and arranged to facilitate the firing order of 1-3-2-4. Fig. 22 is an iεolated, εchematic, εide elevational view and Fig. 23 iε an iεclated, schematic, front elevational view of the four stroke crankshaft 320 for the engine 302, in accordance with the second example of the fourth preferred embodiment of the present invention. The crankshaft 320 includes main bearing journals 322a-e that are connected to rod bearing journals 324a-d by crank-arms 326a-h. The rod bearing journals 324a,b are preferably out of phaεe from the rod bearing journals 324c,d by the angle "b" (Fig. 23) that is preferably 180 degrees of crankshaft revolution. A first connecting rod (not shown) iε connected between the rod bearing journal 324a and a first piston (not shown) disposed within the first cylinder (Fig. 21). The second cylinder (Fig. 21) is εimilarly aεεociated with the rod bearing journal 324b. The third cylinder (Fig. 21) is similarly associated with the rod bearing journal 324c. The fourth cylinder (Fig. 21) is similarly associated with the rod bearing journal 324d. When oriented as depicted in Fig. 23, the crankshaft 320 preferably rotates clockwise.

In accordance with the third example of the fourth embodiment, the engine 302 includes a two stroke crankshaft (not shown) that is similar to the crankshaft 320. The two stroke crankshaft is conεtructed and arranged to facilitate the firing order of 1-3-2-4. The two stroke crankshaft differs from the crankshaft 320 by virtue of the fact that, when the two stroke crankshaft is viewed from the front and is rotating clockwise, the rod bearing journal associated with the third cylinder follows the rod bearing journal asεociated with the first cylinder by 90 degrees, the rod bearing journal asεociated with the εecond cylinder followε the rod bearing journal associated with the first cylinder by 180 degrees, and the rod bearing journal associated with the fourth cylinder follows the rod bearing journal associated with the first cylinder by 270 degreeε.

Fig. 24 iε a εchematic flow diagram of portions of four engines 302a-d (also see Figs. 21-23), in accordance with a fourth example of the fourth embodiment of the present invention. The engineε 302a- d are equipped with intake manifoldε 300a-d (also see Fig. 21), respectively. The engines 302a-d are further equipped with exhaust manifolds 300e-h (also see Fig. 21), respectively. The manifolds 300a-h include first level bifurcations (for example see firεt level bifurcations 304 in Fig. 21). The manifolds 300a-h further include second level bifurcations 312a-h, respectively. The second level bifurcations 312a-h include primary passages 318a-h, reεpectively.

In accordance with the fourth example of the fourth embodiment of the present invention, the intake manifolds 300a-d are part of a composite intake manifold 400. The composite intake manifold 400 further includes third level bifurcation members 402a,b which include primary pasεages 404a,b, respectively. The composite intake manifold 400 further includes a fourth level bifurcation member 406 that includes a primary pasεage 408.

In accordance with the fourth example of the fourth embodiment of the preεent invention, the exhaust manifoldε 300e-h are part of a compoεite exhaust manifold 410. The composite exhauεt manifold 410 further includeε third level bifurcation members 412a,b which include primary pasεages 414a,b, respectively. The compoεite intake manifold 410 further includeε a fourth level bifurcation member 416 that includeε a primary paεεage 418.

In accordance with the fourth example of the fourth embodiment of the preεent invention, the engineε 302a-d are four stroke engines, and each of the engines has a sequential and even firing order of 1-3-2-4. Therefore, it should be understood from the above discussion that each of the primary pasεageε 318a-h haε a pulεe interval of 180 degreeε of crankεhaft revolution. In accordance with the fourth example of the fourth embodiment of the present invention, the engines 302a-d operate 45 degrees of crankshaft revolution out of phase. The first cylinder of the engine 302a fires 45 degrees before the first cylinder of the engine 302c fireε. The firεt cylinder of the engine 302a fires 90 degrees before the first cylinder of the engine 302b fires. The first cylinder of the engine 302a fires 135 degrees before the first cylinder of the engine 302d fires. The pulse intervals of the primary pasεages 318a-d are 90 degrees of crankshaft revolution out of phase. The primary passages 404a, define pulse intervals of 90 degrees of crankshaft revolution. The pulεe intervals of the primary passageε 404a,b are 45 degrees of crankshaft revolution out of phase. The pulse interval of the primary pasεage 408 is 45 degrees of crankshaft revolution. Similarly, the pulse intervals of the primary pasεageε 318e-h are 90 degrees of crankshaft revolution out of phase. The primary passages 414a,b define pulse intervalε of 90 degrees of crankεhaft revolution. The pulse intervals of the primary passages 414a,b are 45 degrees of crankshaft revolution out of phase. The pulse interval of the primary passage 418 is 45 degreeε of crankεhaft revolution. Fig. 25 is a schematic flow diagram of a manifold 430 and portions of a V-4 cylinder engine 432, wherein paired cylinders are adjacent, in accordance with another example of the fourth preferred embodiment of the preεent invention. In accordance with thiε example, the engine 432 haε a εequential and even firing order of 1-4-3-2. The manifold 430 includeε first level bifurcation members 434a-b and a second level bifurcation member 436, all of which furcation members define passages that are interconnected as indicated by the figure. In accordance with this example, the engine 430 is preferably a two stroke engine.

Fig. 26 is a schematic flow diagram of a manifold 330 and portions of a V-6 cylinder engine 332, wherein paired cylinders are adjacent, in accordance with another example of the fourth preferred embodiment of the present invention. In accordance with this example, the engine 330 has a sequential and even firing order of 1-4-5-3-2-6. The manifold 330 includes first level bifurcation members 334a-c and a second level trifurcation member 342, all of which furcation members define passages that are interconnected as indicated by the figure. In accordance with thiε example, the engine 332 is preferably a two stroke engine.

Fig. 27 is a schematic flow diagram of a manifold 352 and portions of a V-8 cylinder engine 354, wherein paired cylinders are adjacent, in accordance with another example of the fourth preferred embodiment of the present invention. In accordance with this example, the engine 354 has a sequential and even firing order of 1-5-4-8-3-7-2-6. The manifold 352 includes first level bifurcations 356a-d, second level bifurcations 358a,b, and a third level bifurcation member 360, all of which furcation members define passages that are interconnected as indicated by the figure. In accordance with this example, the engine 352 is a two stroke engine.

Fig. 28 is a schematic flow diagram of a manifold 370 and portions of a V-6 cylinder engine 372, wherein paired cylinderε are adjacent, in accordance with another example of the fourth preferred embodiment of the preεent invention. In accordance with thiε example, the engine 372 haε a sequential and even firing order of 1-5-3-2-6-4. The manifold 370 includes first level bifurcations 374a-c and a second level trifurcation member 376, all of which furcations define passages that are interconnected aε shown in the figure. In accordance with an alternate embodiment the engine 372 is a two stroke engine that has a sequential and even firing order of 1-5-3-2-6-4. The manifolds of the present invention function to enhance engine operation. For example, Figs. 29-36 are additional schematic flow diagrams of the manifold 300 and portions of the four stroke, four cylinder engine 302, in accordance with the εecond example of the fourth preferred embodiment of the present invention. The engine 302 and manifold 300 were discusεed above with reference to Figs. 21-23. Fig. 21 should be viewed along with the Figs. 29-36 because the passages of the manifold 300 are not labeled in Figs. 29-36 in an effort to clarify the views. The relationships demonstrated in Figs. 29-36 apply to all of the preferred embodiments of the present invention.

Figε. 29-36 εchematically depict relative pressures and flows within the manifold 300 at specific periods of time during the firing sequence of the engine 302. In Figs. 29-32 the manifold 300 is an intake manifold, and in Figs. 33-36 the manifold 300 is an exhaust manifold. Throughout Figs. 29-36, a plus mark (+) denotes a level of positive (i.e., higher than atmoεpheric) pressure within a passage and a minus mark (-) denotes a level of negative (i.e., lower that atmospheric) pressure within a passage. The greater the number of plus marks the higher the presεure within a paεεage, and the greater the number of minus marks, the lesser the presεure within a paεεage. The mark (either pluε or minuε) or group of marks closest to a pasεage εignify the pressure in that passage. Throughout the Figs. 29-36, the arrows closest to a passage indicates the direction of flow in that pasεage. Throughout the Figε. 29-36, where the εymbol o is included in a cylinder, that cylinder iε in fluid communication with the εecondary paεεage of the first level bifurcation member asεociated with that cylinder (e.g., the valve is open). For example, in Fig. 29, the secondary passage 306a (Fig. 21) is in fluid communication with the first cylinder. Where the figure o is not included in a cylinder, that cylinder is not in fluid communication with the secondary passage of the first level bifurcation member associated therewith (e.g., the valve is closed). For example, in Fig. 29, the secondary passage 308a (Fig. 21) is not in fluid communication with the second cylinder.

In Fig. 29, the engine 302 and intake manifold 300 are depicted at 45 degreeε of crankεhaft rotation after the piston in the first cylinder was at top dead center. When the piston in the first cylinder is at top dead center, that piston is at its highest point in the cylinder. As depicted in Fig. 29, the first cylinder has been open to its associated secondary pasεage for 45 degrees of crankshaft revolution and will close after 255 additional degrees of crankshaft revolution; the second cylinder opens to its associated secondary passage in 315 additional degrees of crankshaft revolution and has been closed for 105 degrees of crankεhaft revolution; the third cylinder opens to its associated εecondary passage in 135 additional degrees of crankshaft revolution and has been closed for 285 degrees of crankshaft revolution; and the fourth cylinder has been open to its asεociated secondary passage for 225 degreeε of crankshaft revolution and will close after 75 additional degrees of crankshaft revolution. In Fig. 30-32, the engine 302 and intake manifold 300 are depicted at 225, 405, and 585 degrees of crankshaft revolution, respectively, after the piston in the first cylinder was at top dead center. In the example of Figs. 29-32, communication between a cylinder and its asεociated εecondary passage occurs for a duration of 300 degrees of crankshaft revolution. Figs. 29-32 depict certain characteristics of the present invention that tend to enhance engine operation. For example, in accordance with the preferred embodiments of the present invention, paired cylinders are not simultaneouεly fluidly communicating with their common bifurcation member. Thuε, paired cylinders do not compete with one another for gas drawn through the intake manifold 300. As a further example, in accordance with the preferred embodiments, the back¬ flow generated by one cylinder of a pair of cylinders tends to aid in the filling of the other cylinder of the pair of cylinderε. Thiε phenomena is εchematically repreεented in Figs. 29-32 by the fact that the arrows which identify the direction of flow in secondary pasεages not fluidly communicating with cylinders are oriented toward connected secondary paεεage that are fluidly communicating with a cylinder. In Fig. 33, the engine 302 and exhauεt manifold 300 are depicted at 45 degrees of crankshaft rotation after the piεton in the firεt cylinder waε at top dead center. Aε depicted in Fig. 33, the firεt cylinder haε been closed to itε aεεociated secondary paεsage for 285 degrees of crankεhaft revolution and will open after 135 additional degreeε of crankεhaft revolution. The εecond cylinder has been open to itε aεsociated secondary passage for 225 degrees of crankshaft revolution and closeε to itε aεsociated secondary pasεage in 75 additional degrees of crankshaft revolution. The third cylinder openε to itε associated secondary pasεage in 315 additional degrees of crankshaft revolution and has been closed to its aεεociated εecondary passage for 105 degrees of crankshaft revolution. The fourth cylinder has been open to its associated secondary passage for 45 degrees of crankεhaft revolution and will cloεe after 225 additional degreeε of crankεhaft revolution. In Fig. 34-36, the engine 302 and exhaust manifold 300 are depicted at 225, 405, and 585 degrees of crankεhaft revolution, respectively, after the piston in the first cylinder was at top dead center. In the example of Figs. 33-36, communication between a cylinder and its associated secondary paεεage occurε for a duration of 300 degrees of crankεhaft revolution.

Figs. 33-36 depict certain characteristicε of the preεent invention that tend to enhance engine operation. For example, in accordance with the preferred embodimentε of the present invention, paired cylinders are not simultaneously fluidly communicating with their common bifurcation members. Thus, in accordance with the preferred embodiments of the present invention, paired cylinderε do not tend to force exhaust gasses into one another or compete for a place to discharge gaεeε. Further, flow through a firεt secondary passage of a furcation member into the primary passage of that furcation member tends to draw gasses out of a second εecondary passage of that furcation member. This temporarily decreases the pressure in that second secondary passage, which decrease in presεure enhances the exhausting of the reεpective cylinder into that second εecondary passage.

In accordance with an alternate embodiment of the present invention, a trifurcation member or multiples of trifurcation members are dispoεed at the first level of a manifold, wherein each trifurcation member includes a primary pasεage that brancheε into three secondary pasεageε. In accordance with thiε first alternate embodiment of the present invention, a three cylinder engine would have one first level trifurcation member, a six cylinder engine would have two first level trifurcation members, and a nine cylinder engine would have three first level trifurcation members. In accordance with thiε alternate embodiment, engines or groups of engines with a number of cylinders that are multiples of three would have multiple first level trifurcation members. In accordance with this alternate embodiment of the present invention, manifolds include additional levels of furcation members until the manifold reduces to a single paεεage. Given a repreεentative first level trifurcation member, and a plurality of working chambers that define a sequential firing order, in accordance with this alternate embodiment, the first secondary paεεage of that trifurcation member is preferably connected to a firεt working chamber of the plurality of working chambers. The second secondary paεsage of that trifurcation member is preferably connected to a second working chamber of the plurality of working chambers, wherein the second working chamber fires one third of the way through the firing order after the first W WL jV i i^ il litU C.l_ • I--I --.-LII---. .J. Λ- J , (-lit-. U1 1 C^W lUUJ. J passage of that trifurcation member is preferably connected to a third working chamber of the plurality of working chambers, wherein the third working chamber fires one third of the way through the firing order after the second working chamber. For a four stroke engine, each of the secondary passageε of the repreεentative firεt level trifurcation member have a pulεe frequency of 720 degrees of crankshaft revolution. Further, each of the secondary paεεageε of the repreεentative firεt level trifurcation member are phased 240 degrees apart. The primary passage of the representative trifurcation member has a pulse frequency of 240 degrees of crankshaft revolution. In accordance with another alternate embodiment of the preεent invention, the engine the repreεentative first level trifurcation member iε aεεociated with iε a two stroke engine, wherein the engine and first level trifurcation member cooperate to define pulεe intervalε that are related to thoεe defined immediately above. Each of the pulεe intervalε identified immediately above iε divided by two to calculate the pulεe intervalε associated with that two stroke engine.

Application εerial number 08/288,452, filed in the US on Auguεt 9, 1994, is incorporated by reference, in its entirety.

While the embodiments of the present invention which have been discloεed herein are the preferred formε, other embodimentε of the method and apparatuε of the preεent invention will εuggest themselves to persons skilled in the art in view of thiε disclosure. Therefore, it will be understood that variations and modifications can be effected within the spirit and scope of the invention and that the scope of the present invention should only be limited by the claims below. It is also understood that any relative relationships shown on the drawings are given as preferred relative relationships, but the scope of the invention is not to be limited thereby.

Claims

1. A manifold for a machine, wherein the machine includes a plurality of working chambers that define a εequential firing order, and wherein the plurality of working chamberε include more than four working chamberε, the manifold compriεing: a plurality of bifurcation memberε, wherein each bifurcation member of said plurality of bifurcation members defines a firεt paεεage, a εecond paεεage, and a third passage communicating at and extending from a common location, and wherein said plurality of bifurcation members includes a firεt bifurcation member, wherein said firεt passage of said first bifurcation member is for extending toward and fluidly communicating with a first chamber of the plurality of working chambers, and wherein said second passage of said first bifurcation member iε for extending toward and fluidly communicating with a εecond chamber of the plurality of working chambers that is half way through the firing order from the first chamber of the plurality of working chamberε, wherein said plurality of bifurcation members further includes a second bifurcation member, wherein said first pasεage of εaid εecond bifurcation member iε for extending toward and fluidly communicating with a third chamber of the plurality of working chamberε, and wherein said second passage of said εecond bifurcation member iε for extending toward and fluidly communicating with a fourth chamber of the plurality of working chambers that iε half way through the firing order from the third chamber of the plurality of working chamberε, and wherein said plurality of bifurcation members further includes a third bifurcation member, wherein said first pasεage of εaid third bifurcation member iε for extending toward and fluidly communicating with a fifth chamber of the plurality of working chambers, and wherein εaid second -D<± -

paεεage of εaid third bifurcation member is for extending toward and fluidly communicating with a sixth chamber of the plurality of working chambers that is half way through the firing order from the fifth chamber of the plurality of working chambers.

2. The manifold of claim 1, further comprising an additional member connected to said first bifurcation member, εaid second bifurcation member, and said third bifurcation member, wherein said additional member defineε a void therein that iε in fluid communication with εaid third paεsage of εaid first bifurcation member, said third pasεage of said second bifurcation member, and said third passage of said third bifurcation member. 3. The manifold of claim 2, wherein said additional member defines a first passage, and a second pasεage communicating at and extending from a common location, wherein εaid firεt passage of said additional member extendε to and iε in fluid communication with said third pasεage of εaid first bifurcation member, and wherein said second paεεage of εaid additional member extendε to and iε in fluid communication with εaid third passage of said εecond bifurcation member.

4. The manifold of claim 3, wherein εaid additional member further defines a third passage communicating at and extending from said common location of εaid additional member, wherein εaid third paεεage of εaid additional member extends to and iε in fluid communication with εaid third paεεage of εaid third bifurcation member.

5. The manifold of claim 2, wherein εaid plurality of bifurcation members further includes a fourth bifurcation member, wherein said first passage of said fourth bifurcation member is for extending toward and fluidly communicating with a seventh chamber of the plurality of working chambers, and wherein said second pasεage of εaid fourth bifurcation member is for extending toward and fluidly communicating with an eighth chamber of the plurality of working chambers that is half way through the firing order from the seventh chamber of the plurality of working chambers, and wherein said additional member includes a fifth bifurcation member defining a firεt passage, a second paεεage, and a third paεsage communicating at and extending from said a common location, wherein said first passage of said fifth bifurcation member extends to and is in fluid communication with said third pasεage of εaid first bifurcation member, and wherein said εecond passage of said fifth bifurcation member extends to and is in fluid communication with said third passage of said second bifurcation member, wherein said additional member further includes a sixth bifurcation member defining a first pasεage, a second passage, and a third passage communicating at and extending from a common location, wherein said first passage of said sixth bifurcation member extends to and is in fluid communication with said third passage of said third bifurcation member, and wherein said second passage of said sixth bifurcation member extends to and is in fluid communication with said third passage of said fourth bifurcation member.

6. The manifold of claim 5, wherein said additional member further includeε a seventh bifurcation member defining a firεt paεsage, a second passage, and a third pasεage communicating at and extending from a common location, wherein εaid first passage of said seventh bifurcation member extends to and is in fluid communication with said third paεsage of said fifth bifurcation member, and wherein said second paεsage of said seventh bifurcation member extends to and is in fluid communication with εaid third passage of said εixth bifurcation member. 7.In combination: a machine with a plurality of working chambers, wherein said plurality .of working chambers includeε more than four working chamberε, wherein εaid plurality of working chambers define a sequential firing order, wherein each chamber of said plurality of working chamberε includes a port, and wherein said plurality of working chamberε includeε a firεt chamber, a εecond chamber, a third chamber, a fourth chamber, a fifth chamber, and a sixth chamber; and a manifold including a plurality of bifurcation memberε, wherein each bifurcation member of said plurality of bifurcation members defines a first pasεage, a εecond passage, and a third passage communicating at and extending from a common location, and wherein said plurality of bifurcation members includes a first bifurcation member, wherein said first pasεage of εaid first bifurcation member extends toward and fluidly communicates with a first chamber of said plurality of working chambers, and wherein said second pasεage of said first bifurcation member extends toward and fluidly communicates with a second chamber of said plurality of working chambers that iε half way through εaid firing order from said first chamber of said plurality of working chamberε, wherein said plurality of bifurcation members further includes a second bifurcation member, wherein said first passage of said second bifurcation member extends toward and fluidly communicateε with a third chamber of εaid plurality of working chamberε, and wherein εaid second pasεage of εaid εecond bifurcation member extends toward and fluidly communicates with a fourth chamber of said plurality of working chamberε that iε half way through εaid firing order from εaid third chamber of εaid plurality of working chambers, and wherein εaid plurality of bifurcation members further includes a third bifurcation member, wherein said first passage of εaid third bifurcation member extendε toward and fluidly communicates with a fifth chamber of said plurality of working chambers, and wherein said second paεεage of εaid third bifurcation member extendε toward and fluidly communicateε with a εixth chamber of said plurality of working chambers that is half way through said firing order from said fifth chamber of said plurality of working chambers.

8. The combination of claim 7, wherein εaid manifold and εaid machine are constructed and arranged and cooperate such that each working chamber of said plurality of working chambers has substantially similar cycle to cycle breathing characteriεticε for a given working chamber. 9.The combination of claim 7, wherein εaid manifold further compriseε an additional member connected to εaid firεt bifurcation member, εaid second bifurcation member, and said third bifurcation members, wherein said additional member defines a pasεage therein that extendε to and iε in fluid communication with εaid third paεεage of εaid firεt bifurcation member, εaid third paεεage of εaid εecond bifurcation member, and εaid third paεεage of said third bifurcation member. 10. The combination of claim 9, wherein said machine iε an internal combustion engine and wherein said plurality of working chambers is a plurality of cylinders.

11. The combination of claim 9, wherein said machine includes multiple internal combuεtion engines and wherein said plurality of working chambers is a plurality of cylinders.

12. The combination of claim 10, wherein said manifold is an intake manifold. 13. The combination of claim 10, wherein εaid manifold iε an exhauεt manifold. 14. The manifold of claim 9, wherein said additional member defines a first paεεage, and a εecond paεsage communicating at and extending from a common location, wherein said first pasεage of said additional member extends to and is in fluid communication with said third passage of said firεt bifurcation member, and wherein said second pasεage of εaid additional member extendε to and iε in fluid communication with εaid third paεεage of said second bifurcation member. 15. The manifold of claim 14, wherein said additional member further defines a third paεεage communicating at and extending from said common location of said additional member, wherein said third passage of said additional member extends to and is in fluid communication with said third pasεage of εaid third bifurcation member.

16. In combination: an internal combustion engine that includes a plurality of working chambers and defines a εequential firing order, wherein each chamber of εaid plurality of working chamberε includes a port, and wherein said plurality of working chambers includes a first chamber, a εecond chamber that is adjacent to and half way through said firing order from said first chamber, a third chamber, and a fourth chamber that is adjacent to and half way through said firing order from εaid third chamber; and a manifold including a plurality of bifurcation members, wherein each bifurcation member of said plurality of bifurcation members defineε a first passage, a second passage, and a third pasεage communicating at and extending from said bifurcation member, and wherein εaid plurality of bifurcation members includes a first bifurcation member, wherein said first pasεage of said first bifurcation member extends toward and fluidly communicates with said port of said first chamber, and wherein said second passage of said first bifurcation member extendε toward and fluidly communicates with εaid port of εaid second chamber, wherein said plurality of bifurcation members further includes a second bifurcation member, wherein εaid first passage of said second bifurcation member extends toward and fluidly communicates with said port of said third chamber, and wherein said second passage of said second bifurcation member extends toward and fluidly communicates with said port of said fourth chamber. 17. The combination of claim 16, wherein said manifold and said engine are constructed and arranged and cooperate such that each working chamber of said plurality of working chambers has subεtantially similar cycle to cycle breathing characteristics for a given working chamber.

18. The combination of claim 16, wherein said internal combustion engine includes multiple internal combustion engines.

19. The combination of claim 16, wherein said manifold further comprises an additional member connected to said first bifurcation member, said second bifurcation member, and said third bifurcation members, wherein said additional member defineε a passage therein that extends to and is in fluid communication with said third passage of said first bifurcation member, and said third pasεage of εaid εecond bifurcation member.

20. The combination of claim 19, wherein said manifold iε an intake manifold. 21. The combination of claim 19, wherein εaid manifold iε an exhauεt manifold.

22. The manifold of claim 19, wherein said additional member defines a first passage, a second passage, and a third pasεage communicating at and extending from a common location, wherein εaid first pasεage of said additional member extends to and is in fluid communication with said third passage of said first bifurcation member, and wherein said second passage of said additional member extends to and is in fluid communication with εaid third paεεage of εaid εecond bifurcation member.

23. A method of coordinating pulεes in a manifold that includes a plurality of bifurcation members, wherein each bifurcation member of the plurality of bifurcation members defines a firεt passage, a second passage, and a third passage communicating at and extending from a common location, and wherein the plurality of bifurcation members includes a first bifurcation member, a second bifurcation member, and a third bifurcation member, and wherein the manifold further includes a fourth member that fluidly connects the third passageε of the first, second and third bifurcation members, the method comprising stepε of: creating a first pulse in the first pasεage of the firεt bifurcation member, creating a εecond pulεe in the first pasεage of the second bifurcation member after the step of creating a first pulse, creating a third pulse in the first passage of the second bifurcation member after the step of creating a second pulse, creating a fourth pulse in the second pasεage of the first bifurcation member after the step of creating a third pulse, creating a fifth pulse in the second passage of the second bifurcation member after the step of creating a fourth pulse, and creating a sixth pulεe in the second passage of the third bifurcation member after the step of creating a fifth pulse.

24. The method of claim 23, further comprising a step of repeating the steps of creating so that for each bifurcation member pulse intervals are defined in the first passage and second pasεage, wherein for each bifurcation member a pulεe interval is defined in the third passage that is half of the pulse intervals defined in the firεt paεsages and second paεsages.

25. The method of claim 24, wherein the fourth member defines a primary passage that branches into and fluidly communicateε with the third paεεage of the firεt bifurcation member, and the third passage of second bifurcation member, wherein the primary pasεage haε a pulεe interval that iε half of the pulse intervalε defined in the third paεεageε.

26. The method of claim 24, wherein the fourth member defineε a primary paεεage that brancheε into and fluidly communicates with the third passage of the first bifurcation member, the third passage of second bifurcation member, and the third passage of the third bifurcation member, wherein the primary pasεage haε a pulse interval that is a third of the pulse intervals defined in the third passages.

27. A manifold for a machine, the manifold comprising: a plurality of bifurcation members wherein said plurality of bifurcation members includes a first bifurcation member, a second bifurcation member, and a third bifurcation member, wherein each bifurcation member of εaid plurality of bifurcation memberε includes a plurality of pasεageε consisting essentially of a first passage, a second paεsage, and a third passage communication at and extending from a common location, and wherein for any given bifurcation member of said plurality of bifurcation members, said common location of said given bifurcation member provides substantially the sole direct communication between εaid plurality of paεεages of said given bifurcation member, and a trifurcation member wherein said trifurcation member includes a plurality of pasεages consisting esεentially of a first passage, a second paεεage, a third passage and a fourth paεsage communicating at and extending from a common location, wherein said common location of said trifurcation member provideε εubεtantially the εole direct communication between εaid plurality of passageε of εaid trifurcation member, wherein said first passage of said trifurcation member is connected to and communicates with said third passage of said firεt bifurcation member εuch that εaid firεt passage of trifurcation member directly communicates substantially solely between passages of said plurality of pasεages of said first bifurcation member and εaid first pasεage of said trifurcation member, wherein said second paεsage of said trifurcation member is connected to and communicates with said third passage of said second bifurcation member such that said second passage of said trifurcation member directly communicates substantially solely between pasεageε of εaid plurality of passages of said trifurcation member and said third pasεage of said second bifurcation member, and said third pasεage of εaid εecond bifurcation member directly communicateε εubεtantially εolely between paεεageε of εaid plurality of passages of said second bifurcation member and εaid εecond paεεage of εaid trifurcation member, and wherein said third passage of said trifurcation member is connected to and communicates with said third passage of said third bifurcation member such that said third passage of said trifurcation member directly communicateε substantially solely between pasεageε of εaid plurality of passages of said trifurcation member and said third passage of said third bifurcation member, and εaid third paεsage of said third bifurcation member directly communicates substantially solely between pasεages of said plurality of passages of said third bifurcation member and said third passage of said trifurcation member.

28. The manifold of claim 27, wherein said firεt paεεageε and εaid second passages of said plurality of bifurcation memberε define diameters, wherein εaid of bifurcation members and said firεt paεεage, said second passage, and said third passage of trifurcation member define diameters that are greater than said diameters of said first pasεages and said second pasεages of said plurality of bifurcation members, and wherein said fourth pasεage of said trifurcation member defines a diameter that is greater that said diameters of said third passages of said plurality of bifurcation members and said first pasεage, εaid εecond passage, 0and said third pasεage of εaid trifurcation member.

29. A manifold for a machine, the manifold compriεing: plurality of bifurcation memberε wherein εaid plurality of bifurcation memberε includes a first bifurcation member, a second bifurcation member , as third 5bifurcation member, a fourth bifurcation member, a fifth bifurcation member, a sixth bifurcation member and a seventh bifurcation member, wherein each bifurcation member of said plurality of bifurcation members includes a plurality of passage consisting 0 essentially of a first passage, a second pasεage, and a third paεsage communicating at and extending from a common location, wherein for any given bifurcation member of εaid plurality of bifurcation members, said common location of said given bifurcation member 5 provides substantially the εold direct communication between a plurality of paεsages of said given bifurcation member, and wherein said first passage of said fifth bifurcation member it connected to and communicates with said third pasεage of said first 0 bifurcation member εuch that εaid firs paεεage of εaid fifth bifurcation member directly communicateε εubεtantially εolely between passageε of said plurality of passageε of εaid firεt bifurcation member, and εaid third passage of said first bifurcation member directly 5 communicateε εubεtantially εolely between paεεageε of εaid plurality of paεεageε of εaid firεt bifurcation member and εaid first passage of said fifth bifurcation member, wherein said εecond paεεage of said fifth bifurcation member is connected to and communicates with said third passage of said second bifurcation member such that said second passage of said fifth bifurcation member directly communicates substantially solely between passages of said plurality of passages of said fifth bifurcation member and said third passage of said second bifurcation member, and said third passage of said second bifurcation member directly communicates substantially solely between paεεageε of εaid plurality of paεεageε of said εecond bifurcation member and said second paεεage of εaid fifth bifurcation member, wherein εaid firεt paεsage of said εixth bifurcation member iε connected to and communicates with said third pasεage of εaid third bifurcation member εuch that εaid firεt paεsage of said sixth bifurcation member directly communicates substantially solely between passages of said plurality of passages of said sixth bifurcation member and said third paεεage of εaid third bifurcation member and εaid third paεsage of said third bifurcation member directly communicates subεtantially εolely between paεεages of said plurality of paεεageε of aid third bifurcation member and said first paεεage of said sixth bifurcation member, wherein said second pasεage of εaid εixth bifurcation member iε connected to and communicateε with said third passage of said fourth bifurcation member such that εaid εecond paεsage of said sixth bifurcation member directly communicates subεtantially εolely between passages of said plurality of paεεageε of εaid εixth bifurcation member and εaid third paεεage of εaid fourth bifurcation member, and εaid third passage of said fourth bifurcation member directly communicates subεtantially εolely between paεεageε of εaid plurality of paεεages of said fourth bifurcation -D3-

said plurality of pasεageε of said fourth bifurcation member and said second passage of said fourth bifurcation member and said second pasεage of said sixth bifurcation member, wherein said first passage of said seventh bifurcation member is connected to and communicate with said third passage of said fifth bifurcation member such that said firs pasεage of εaid εeventh bifurcation member directly communicates subεtantially solely between passages of said plurality of passages of said seventh bifurcation member and said third pasεage of εaid fifth bifurcation member, and εaid third paεsage of said fifth bifurcation member, and said third pasεage of εaid fifth bifurcation member directly communicateε substantially solely between pasεageε of εaid plurality of passages of said fifth bifurcation member and said firεt passage of said seventh bifurcation member, and wherein said second pasεage of aid εeventh bifurcation member is connected to and communicates with said third paεsage of said sixth bifurcation member such that said second passage of said seventh bifurcation member directly communicates substantially solely between passages of said plurality of passages of said seventh bifurcation member and said third passage of said εixth bifurcation member directly communicateε substantially solely between pasεageε of said plurality of passages of said sixth bifurcation member and said second passage of said seventh bifurcation member.

30. The manifold of claim 29, wherein said first passages and said second passages of said first, second, third and fourth bifurcation members define diameters, wherein said third pasεageε of εaid first, second, third and fourth bifurcation members and said first and second passages of said fifth and sixth bifurcation members define diameters that are greater than said diameters of said firεt paεεageε and second 31. In combination: a reciprocating piεton machine with a plurality of workcha bers, wherein said reciprocating piston machine includes a crankshaft and a plurality of workchambers, wherein εaid plurality of workchamberε includes an even number of workchambers greater than four, and wherein said reciprocating piston machine defines a sequential breathing order wherein each workchamber of said plurality of workchambers includes a port, and a manifold defining, a plurality of firεt level paεεageε in a quantity equal to the number of workchamberε, wherein each first level of pasεage of said plurality of first level passageε communicateε with an individual workchamber of said plurality of workchambers such that each first level pasεage of εaid plurality of firεt level paεεageε receiveε a pulse every time εaid crankεhaft rotateε a number of degreeε said crankshaft rotates from the beginning of εaid breathing order to the end of εaid breathing order, and a plurality of εecond level paεεageε in a quantity equal to one-half the number of workchamberε, wherein each εecond level paεsage of said plurality of second level pasεages branches into two firεt level passages of said plurality of first level pasεageε, wherein said manifold is constructed and arranged and cooperates with εaid machine εuch that each second level pasεage of εaid plurality of εecond level passages receives a pulse every time said crankshaft rotateε a number of degrees that is approximately equal to the number of degreeε εaid crankshaft rotates from the beginning of said breathing order to half way through said breathing order, and all of the pulεes within each individual second level passage of said plurality of second level passages are separated by a number of degreeε that iε approximately equal to the number of degrees said crankshaft rotates from the beginning of said breathing order to half way equal to the number of degrees said crankshaft rotates from the beginning of said breathing order to half way through said breathing order.

32. The combination of claim 31, wherein said plurality of workchambers includes a first workchamber, and a second workchamber that is adjacent to and half way through said breathing order from said first workchamber, and a third workchamber, and a fourth workchamber that is adjacent to and half way through said breathing order from said third workchamber, and wherein said first workchamber of said plurality of workchambers and said second workchamber of said plurality of workchambers breathe through a first distribution εection of said plurality of distribution sections, and wherein said third workchamber of εaid plurality of workchambers and said fourth workchamber of said plurality of workchambers breathe through a second distribution section of said plurality of distribution sectionε. 33. The combination of claim 31, wherein εaid manifold further includes an additional pasεage wherein at least two second level pasεageε of said plurality of second level passages branch into said additional pasεage. 34. In combination: an internal combuεtion engine wherein εaid internal combuεtion engine includes a crankshaft and a plurality of workchambers, wherein said plurality of workchambers includes an even number of workchambers greater than four, and wherein said internal combuεtion engine defines a sequential firing order, and a manifold defining a plurality of first level passages in a quantity equal to the number of workchambers, wherein each first level pasεage of εaid plurality of firεt level passages communicates with an individual workchamber of said plurality of workchambers such that each first level pasεage of εaid plurality of first level pasεages receives a pulse every time said crankεhaft rotateε a number of degrees that is approximately equal to the number of degreeε said crankshaft rotates from the beginning of εaid firing order to the end of εaid firing order, and a plurality of second level passageε in a quantity equal to one-half the number of workchamberε, wherein each εecond level passage of said plurality of second level passages branches into two first level pasεageε of said plurality of first level passages, and wherein said manifold iε conεtructed and arranged and cooperateε with εaid engine εuch that each εecond level paεsage of said plurality of second level pasεageε receives a pulse every time said crankshaft rotates a number of degreeε that is approximately equal to the number of degrees said crankshaft rotates from the beginning of said firing order to half way through said firing order, and all of the pulses within each individual second level pasεage of εaid plurality of second level pasεages are separated by a number of degrees that is approximately equal to the number of degreeε εaid crankshaft rotates from the beginning of said firing order to half way through said firing .order.

35. A manifold for a multi-cylinder internal combuεtion engine having a crankεhaft and an even number of cylinderε greater than four and defining a εequential firing order, the manifold defining: a plurality of firεt level paεεages in a quantity equal to the number of cylinders, wherein each level pasεage of εaid plurality for firεt level passages is for communicating with an individual cylinder of the plurality of cylinders such that each first level pasεage of said plurality of first level pasεageε receiveε a pulse every time the crankshaft rotates a number of degreeε that is approximately equal to the number of degrees the crankshaft rotates from the beginning of said firing order to the end of said firing order, and a plurality of second level pasεageε in a quantity equal to one-half the number of cylinderε, wherein each εecond level passage of said plurality of second level pasεages brancheε into two first level pasεages of said plurality of first level pasεageε, and wherein εaid manifold is constructed and arranged and cooperateε such that each second level paεεage of εaid plurality of second level passages receives a pulse every time the crankshaft rotates a number of degrees that is approximately equal to the number of degrees the crankshaft rotates from the beginning of said firing order to half way through said firing order, and all of the pulseε within each individual second level pasεage of εaid plurality of second level pasεages are separated by a number of degreeε that iε approximately equal to the number of degreeε the crankεhaft rotateε from the beginning of εaid firing order to half way through εaid firing order.

36. The manifold of claim 35, wherein each of said second level pasεages of said plurality of second level pasεages are interconnected.

37. The manifold of claim 35, wherein said internal combustion engine includes multiple internal combustion engines.

38. The manifold of claim 35, wherein said manifold is an intake manifold.

39. The manifold of claim 35, wherein said manifold is an exhaust manifold, and εaid internal combuεtion engine has an even firing interval.

40. A manifold for a reciprocating piston machine, wherein said reciprocating piston machine includes a crankshaft and defines a sequential breathing order, the manifold comprising: a plurality of first level passages in a quantity equal to the number of workchamberε, wherein each first level passage of said plurality of first level paεsages communicates with an individual workchamber of said plurality of workchambers such that each first level passage of said plurality of first level passages receives a pulse every time said crankshaft rotates a number of degrees that iε approximately equal to the number of degrees said crankshaft rotates from the beginning of said breathing order to half way through said breathing order, and a plurality of second level paεεageε in a quantity equal to one-half the number of workchamberε, wherein each εecond level passage of said plurality of εecond level paεsages branches into two firεt level passageε of εaid plurality of firεt level paεsages, wherein said manifold is constructed and arranged and cooperates with said machine such that each second level paεεage of εaid plurality of εecond level pasεageε receiveε a pulεe every time said crankshaft rotates a number of degrees that is approximately equal to the number of degrees said crankshaft rotates from the beginning of said breathing order to half way through said breathing order, and all of the pulses within each individual second level pasεage of said plurality of εecond level paεεages are separated by a number of degrees that is approximately equal to the number of degreeε εaid crankεhaft rotateε from the beginning of εaid breathing order to have way through said breathing order.

41. The manifold of claim 40, wherein each of said second level pasεages of said plurality of second level passages are interconnected.

42. The manifold of claim 40, wherein said reciprocating piston machine includes multiple reciprocating piston machines. 43. The manifold of claim 40, wherein said manifold is an intake manifold. and εaid reciprocating piston machine create substantially similar cycle to cycle workchamber compression characteristics for a given workchamber under a given set of remaining conditionε.

47. The method of claim 46, wherein said reciprocating piεton machine iε an internal combuεtion engine, wherein εaid method, said subεtantially similar cycle or cycle workchamber compresεion characteristics for a given workchamber under a given εet of remaining conditionε, and εaid internal combuεtion engine create εubεtantially εimilar cycle to cycle workchamber combuεtion characteriεticε for a given workchamber under a given set of remaining conditions.

48. The method of claim 46, wherein εaid method, εaid εubεtantially similar cycle to cycle workchamber combustion characteristics for a given workchamber under a given set of remaining conditionε, and reciprocating piston machine create subεtantially εimilar cycle to cycle workchamber expanεion characteriεtics for a given workchamber under a given set of remaining conditions.

49. The method of claim 48, wherein said reciprocating piston machine is an internal combustion engine.

50. The method of claim 47, wherein said internal combustion engine includeε multiple internal combuεtion engineε.

51. The method of claim 49, wherein said internal combustion engine includes multiple internal combustion engines.

52. A manifold for a four cylinder internal combustion engine having a crankshaft and defining a sequential firing order, the manifold defining: a plurality of firεt level paεεages in a quantity equal to the number of cylinders, wherein each first level passage of said plurality of firεt level passageε iε for communicating with an individual cylinder of the plurality of cylinderε εuch that each firεt level paεεage of εaid plurality of firεt level passageε receives a pulse every time the crankshaft rotateε a number of degreeε that is approximately equal to the nu ber of degrees the crankshaft rotates from the beginning of said firing order to the end of said firing order, and a plurality of second level pasεageε in a quantity equal to one-half the number of cylinderε, wherein each εecond level paεεage of εaid plurality of εecond level paεεageε brancheε into two first level pasεageε of εaid plurality of firεt level paεεages, and wherein εaid manifold iε constructed and arranged and cooperates such that each second level passage of said plurality of second level pasεages receives a pulse every time the crankshaft rotateε a number of degreeε that iε approximately equal to the number of degrees the crankshaft rotates from the beginning of said firing order to half way through said firing order, and all of the pulseε within each individual second level pasεage of said plurality of second level passageε are εeparated by a number of degrees that is approximately equal to the number of degrees the crankεhaft rotates from the beginning of said firing order to half way through said firing order.

53. The combination of claim 52, wherein said plurality of cylinders includes a firεt cylinder and a εecond workchamber that iε adjacent to and half way through εaid breathing order from εaid firεt workchamber, and a third workchamber, and a fourth workchamber that iε adjacent to and half way through εaid breathing order from εaid third workchamber, and wherein εaid first workchamber of said plurality of workchamberε and said second workchamber of εaid plurality of workchamberε breathe through a firεt distribution section of εaid plurality of diεtribution εectionε, and wherein said third workchamber of said plurality of workchamberε and said fourth workchamber of said plurality of workchambers breathe through a second distribution section of εaid plurality of diεtribution εections.

54. The manifold of claim 52, wherein each of said second level paεεageε of said plurality of second level passages are interconnected. 55. The manifold of claim 52, wherein said internal combustion engine includes multiple internal combustion engines.

56. The manifold of claim 52 wherein said manifold is an intake manifold. 0 57. The manifold of claim 52 wherein said manifold is an exhauεt manifold, and said internal combustion engine has an even firing order.

58. The manifold of claim 56 wherein said pairs of said first level paεsages are located on separate bankε 5 of εaid interal combuεtion engine cylinderε.

59. A crankεhaft for a multi-cylinder internal combuεtion engine having an even number of cylinderε and defining a εequential firing order, the crankεhaft compriεing main bearing journals and connecting rod 0throws: a plurality of connecting rod throws equal to the number of cylinders within a bank of engine cylinderε, wherein εaid connecting rod throwε are grouped in pairs, wherein said individual members of connecting rod throws are located at the same 5 crankεhaft angle degree location and poεitioned adjacent to one anther, wherein the number of said plurality of paired connecting rod throws is equal to the number of cylinders within a bank of cylinders of said internal combustion engine. 0 60. The crankshaft of claim 59, wherein a first pair of adjacent rod throws are poεitioned 180° of crankshaft angle degreeε from a εecond pair of adjacent rod throwε. 61. A crankεhaft for a four cylinder internal combuεtion engine having an even number of cylinders 5 and defining a sequential firing order, the crankshaft compriεing main bearing journals and connecting row throwε: a plurality of connecting rod throwε equal to the number of cylinderε within a bank of engine cylinderε, wherein εaid connecting rod throwε are grouped in pairε, wherein εaid individual connecting rod throws are located 180° of crankshaft angle degrees from one another, wherein a first pair of connecting rod throwε are poεitioned 90° of crankshaft angle degrees from a second pair of connecting rod throws.