Water Jacketed Exhaust Pipe for Marine Exhaust Systems

1. Field of the Invention

The present invention relates generally to a water jacketed exhaust pipe that curtails surface exhaust turbulence near the tail end of an inner liner of the pipe thereby preventing the migration of potentially corrosive water and salt back into the inner liner of the pipe. Additionally, the present invention scatters a stream of water exiting the water jacketed exhaust pipe into a spray which is directed into the exhaust gas path thereby causing superior heat exchange from the coolant to the exhaust gas.

2. Description of the Prior Art

Typically marine engines are cooled by water which is pumped from the ocean or lake through a cooler into the engine and then discharged therefrom into a water jacketed exhaust pipe to cool the exhaust system. Preferably, the exhaust is cooled as far upstream as possible to reduce thermal stress on the downstream exhaust system components. However, the prior art method of cooling the exhaust system by injecting a stream of water into the exhaust stream is crude and inefficient. As shown in FIG. 1, the typical arrangement employs a water jacketed exhaust pipe 2 comprising an outer shell 4, an inner liner 6 and a spray ring 8. The pipe 2 is connected to a heat resistant rubber hose or some other standard exhaust conduit. Near the termination of exhaust pipe 2 a circumferential spray ring 8 is employed between the inner liner 6 and outer shell 4. The spray ring 8 is essentially a washer or partition that separates outer shell 4 from inner liner 6 and impedes water from freely exiting the water jacket volume 5 formed between the outer shell and the inner liner. Generally, spray ring 8 contains a plurality of narrow longitudinal passageways 9 from which coolant can exit volume 5 in the form of a spray or stream. However, the coolant stream exiting water jacket volume 5 is generally streamed along only the outer circumference of the volume of exhaust gas flow as shown in FIG. 1. Accordingly, there is a poor mixture of coolant and exhaust gas and thus poor heat exchange. Subsequently, the exhaust system components downstream of the tail end of the water jacketed exhaust pipe 2 unnecessarily absorb heat that could better be transferred to the water. As a result, these downstream components are subjected to higher temperatures and greater temperature cycling than necessary. Moreover, in light of the production of larger marine engines which run at hotter temperatures, marine exhaust systems are already being subjected to hotter temperatures. Accordingly, there is a need for more efficient ways of cooling a marine exhaust system.

An additional shortcoming of the prior art is corrosion. Specifically, it has been discovered that due to the direction of the exhaust gas flow within inner liner 6 a narrow band of turbulence is created near its inner surface 3. As shown in FIG. 2, turbulence T as a suctioning effect opposite the direction of exhaust gas flow. Accordingly, some of the water exiting spray ring 8 will slowly migrate into inner liner 6 along inner surface 3. Additionally, when the boat is run in the ocean the cooling water will contain salt and other impurities that will also migrate into the inner liner. Unfortunately, the hot exhaust gases which contain hydrogen-sulfide and carbon molecules chemically react with the chloride ions produced from the heated salt water to form acids including a mild sulfuric acid which are deposited on the inner surface 3 of liner 6. These acids, over a short period of time corrode the water jacketed exhaust pipe 2. Presently, the only way to prevent this corrosion is to manufacture the inner liner of a highly expensive material that is resistant to acid corrosion.

Accordingly there is a present need for a improved water jacketed exhaust pipe that provides a superior mixture of coolant and exhaust gas and consequently has better heat exchange characteristics. Additionally, there is a present need for a jacketed exhaust pipe termination which clips the turbulence along the inner surface of the inner liner and thereby prevents water spray from migrating into the inner liner where corrosion can occur.

The water jacketed exhaust pipe termination of the present invention solves the problems encountered by the prior art by the provision of both a first inwardly directed section at the tail end of the inner liner and a second inwardly directed taper at the tail end of the outer shell of the water jacketed exhaust pipe. The first inwardly directed section of the inner liner clips the surface turbulence near the tail end of the inner surface of the inner liner. The second inwardly directed taper near the tail end the outer shell forms a deflection surface which breaks up the water stream and in turn increases heat exchange. Consequently, two significant shortcomings of the prior art have been eliminated without significantly increasing the cost of the pipe.

The first shortcoming eliminated by the present invention is corrosion. Specifically, the first inwardly directed section of the inner liner forms a turbulence barrier that prevents the formation of turbulence near the tail end of the inner surface of the inner liner. In turn, this prevents water and salt from migrating upstream into the inner liner and chemically reacting therein to form acids that are deposited on the inner surface of the inner liner. As a result, the prior art shortcoming of destructive acid deposits that corrode the inner line has been eliminated.

The second significant shortcoming eliminated by the present invention is poor heat exchange. The second inwardly directed taper near the tail end of the outer shell forms a deflection surface for water exiting the spray ring. As such, the spray or stream exiting from the spray ring collides with the inner surface of the inwardly directed taper and is broken down into fine water particles which are deflected into the path of exhaust gas flow. Since the water particles have a much greater surface area than the stream of water ejected from the spray ring and since the particles are deflected directly into the exhaust gas path, the cooling water absorbs far more thermal energy per unit volume than the prior art designs.

Accordingly, the new termination makes the muffler pipe more corrosion resistant and increases the surface area of the water that is forced into the exhaust gas path. In turn, this increases the cooling efficiency of the muffler and provides superior thermal protection to the exhaust system components downstream from the water jacketed pipe termination.

It is therefore a principal object of this invention to provide a water jacketed exhaust pipe termination that breaks the stream of water exiting the water jacket into a spray of variably sized water particles.

It is a further object of this invention to provide a water jacketed exhaust pipe termination that clips surface turbulence along its inner liner.

It is yet another object of this invention to provide a water jacketed exhaust pipe termination that prevents water spray from migrating upstream into the inner liner of the water jacketed exhaust pipe.

It is still another object of this invention to provide a water jacketed exhaust termination that prevents corrosion of the inner liner.

It is still yet another object of this invention to provide a water jacketed exhaust pipe that resists acid corrosion without the use of highly expensive acid resistant materials.

It is an additional object of this invention to provide a more efficient water jacketed exhaust conduit that reduces thermal fatigue to exhaust system components downstream of the water jacketed exhaust pipe.

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

FIG. 1 is a side section view of the prior art device;

FIG. 2 is a partial detailed view of the tail end of the inner and outer liners of the device of FIG. 1;

FIG. 3 is a end view of an embodiment of the present invention depicted in FIG. 4;

FIG. 4 is a side sectional view of an embodiment of the present invention;

FIG. 5 is an end view of an alternate embodiment of the present invention as depicted in FIG. 6;

FIG. 6 is a side sectional view of an alternate embodiment of the present invention;

FIG. 7 is a detailed side sectional view showing the alternate embodiment depicted in FIG. 6;

FIG. 8 is a perspective view of the exhaust exit end of the alternate embodiment depicted in FIG. 7;

FIG. 9 is a perspective view of the exhaust inlet end of the alternate embodiment shown in FIG. 7;

FIG. 10 is an end view of a second alternate embodiment of the present invention;

FIG. 11 is a side sectional view of the second alternate embodiment of the present invention depicted in FIG. 10;

FIG. 12 is a perspective view of the exhaust outlet end of the second alternate embodiment shown in FIGS. 10 and 11;

FIG. 13 is a detailed side sectional view showing the second alternate embodiment depicted in FIGS. 10-12.

With reference to FIG. 4, there is depicted a water jacketed exhaust pipe generally characterized by reference numeral 10. The exhaust pipe 10 generally comprises an inner liner 12 having a first inwardly tapered surface 14, an outer shell 18 having an inwardly tapered surface 20 at tail end 16 and a spray ring 16.

In the preferred embodiment both the inner liner 12 and the outer shell 18 and spray ring 16 are constructed from corrosion resistant metal such as stainless steel for example. The outer shell 18 is generally cylindrical in shape and has a diameter greater than inner liner 12. Between outer shell 18 and inner liner 12 is a spray ring 16 or spacer that separates the outer shell from the inner liner, forming a water jacket volume 24 therebetween. Additionally, spray ring 16 prevents water contained in volume 24 from freely exiting the exhaust pipe 10. Preferably, spray ring 16 contains several narrow longitudinal passageways 28 that allow water to pass from volume 24 to cooling turbulent area 22. In that manner, a back pressure is built up within volume 24 thereby forcefully ejecting water through the longitudinal passageways 28 to cooling turbulent area 22. Although the passageways shown are parallel to the elongate axis of the pipe, it is realized they may be in any direction so long as they fluidly connect volume 24 with an external volume outside the exhaust pipe 10.

In operation the exhaust gas flow shown as E in FIG. 4 is directed toward the left out of the water jacketed exhaust pipe 10. As shown, the exiting exhaust gas E causes turbulence T near the inner surface 26 of inner liner 12. Typically, turbulence T is contained within fractions of an inch from inner surface 26. As a result, the turbulence produces a suction effect that normally tends to attract water ejected from passageways 28 of spray ring 16 onto inner surface 26 of the inner liner. However, as shown in FIG. 4, the first inwardly tapered surface 14 at the tail end of inner liner 12 clips the turbulence and as a result inhibits water from travelling backwards along inner surface 26 of the liner.

An additional advantage of the preferred embodiment is its superior heat exchange properties. Specifically, outer shell 18 is provided with a second inwardly tapered surface 20 at its tail end. Preferably, the second inwardly tapered surface 20 is curved such that over its length it curves almost to the radius of inner liner 12. As a result, second inwardly tapered surface 20 is directly in the path of the water stream ejected through the passageway 28 of the spray ring. Accordingly, as the water exits spray ring 16 it forcefully collides into the second inwardly tapered surface 20 and is broken up/separated into fine water particles. As can be seen in FIG. 4, the water particles have a much greater surface area than did the stream of water exiting spray ring 16. Furthermore, the particles upon colliding with surface 20 are redirected into the central part of the exhaust gas flow shown as turbulent cooling area 22. While in the turbulent cooling area the fine water particles are almost immediately converted into steam thereby taking on an immense amount of kinetic and thermal energy. The energy exchange taking place is immense when compared to the amount of energy absorbed by the prior art designs because a phase change takes place. Specifically, since the fine water particles have a much greater surface area as compared with a stream of water they can better mix with the exhaust gases in cooling area 22 and take on enough kinetic and thermal energy to convert from a liquid phase to a gaseous phase. Consequently, a great deal more energy is removed from the exhaust gas than in prior art designs. In turn, this gas is quickly carried through the remaining downstream sections of the exhaust pipe and expelled from the exhaust system. As a result, the downstream exhaust system components which may be fiberglass or rubber are subjected to significantly less thermal stress and are thus are far less prone to melting or other forms of fatigue that could ultimately end in their failure. For example, as shown in FIG. 2 the tail end of the water jacketed exhaust pipe is connected to a heat resistant silicone based rubber hose 30 via a hose clamp 32. Although hose 30 is normally resistant to high temperatures it has a longer life expectancy when subjected to lower temperatures. Accordingly, another advantage of the present invention is reduced thermal fatigue on exhaust system components downstream from the tail end of the water jacketed exhaust pipe 10.

It is realized that neither the first or second inwardly tapered surfaces 14 and 20, respectively, have to be curved as shown in FIG. 2. Rather, either or both surfaces may be in the form of a cone or any other shape that is generally directed inwardly. Furthermore, the use of the term water in this application is meant to include sea water, lake water and in general any body of water that marine vessels may be operated within.

An additional shortcoming of the prior art is eliminated due to the superior heat exchange properties of the present invention. Typically, a marine engine of an average size boat will pump 90-100 gallons per minute when running at full bore or cruising speed. Accordingly, there is a great deal of water to cool both the engine and exhaust system when the engine is running at this speed. However, when the engine is idling, it is typical that only 15 gallons per minute will be pumped through the exhaust system. In the prior art designs, 15 gallons per minute does not extract a great deal of heat from the exhaust and thus, the exhaust system can be overheated. However, in the present invention, adequate coating still takes place, even when the engine is running at idle and only pumping 15 gallons of water per minute due to the higher efficiency of heat transfer from the exhaust gas E to the water.

It is envisioned that this invention is applicable to both water jacketed pipe and dry pipe. Water jacketed pipe refers to a type of pipe wherein the entire pipe is double-walled from the engine to the tail end and water is communicated from the engine directly into the space between the inner liner and outer shell. On the other hand, a dry pipe is a single-walled pipe wrapped with insulation, wherein only a short section at the very tail end of the pipe contains a double-walled section. In this case, a water can is welded onto the dry pipe and water can be pumped into the tail end of the pipe to be mixed with exhaust in the same manner explained for the water jacketed pipe.

In an alternate embodiment, as shown in FIGS. 5-9, the inner liner 12' extends beyond the outer shell 18'. Spray ring 16' is angled between outer shell 18' and inner liner 12' so that passageways 28' direct water flow from volume 24' onto inner surface 20' of outer shell 18'.

Directing the water flow from passageways 28' directly at the outer shell 18' intensifies the effect of the inwardly tapered surface 20'. The water fans out from passageways 28' and collides with outer shell 18' and inwardly tapered surface 20' and is further broken up/separated into fine water particles. A portion of the water particles are deflected back onto the exterior surface 27' of the inner liner 12' thereby providing a uniform film of water near the termination of the exterior surface 27' of inner liner 12'. The uniform film of water absorbs heat from inner liner 12', and under certain operating conditions will almost instantaneously flash to steam thereby beginning the cooling process even prior to entering the turbulent cooling area 22'.

Passageways 28' in spray ring 16', shown in FIGS. 5-8, are fewer, but larger in diameter than passageways 28 in spray ring 16, shown in FIG. 4. Fewer large diameter passageways increases water flow and the cooling effect is thereby increased. Passageways 28' are spaced such that the streams of water fan out therefrom such that streams from adjacent passageways 28' intersect after contacting outer shell 18' thereby causing a portion of the water to deflect away from outer shell 18' and onto the outer surface 27' of inner liner 12'. Accordingly, it is important that spray ring 16' is spaced a sufficient distance from the termination of the inner liner 12' and outer shell 18', and that passageways 28' are spaced and angled toward outer shell 18' so as to project fanning streams of water such that adjacent streams intersect after contacting outer shell 18' causing a portion of each water stream deflect onto the outer surface 27' of inner liner 12'. In addition, a portion of the water disperses into a substantially uniform film on the inner surface of outer shell 18' and is dispersed as fine particles by inwardly tapered surface 20' into the central part of the exhaust gas flow 22'.

Inner liner 12' extends beyond the end of outer shell 18' into the turbulent cooling area 22'. As in the first embodiment, the inwardly tapered surface 14' of inner liner 12' clips turbulence and thus inhibits water from traveling backward along inner surface 26' of liner 12'. Having inner liner 12' extend into the turbulent cooling area 22', further reduces water flow back along inner surface 26' of the liner.

In an example of supplying water to the present invention, as shown in FIGS. 7-9, water will enter volume 24' via fitting 50' and inlet pipe 48'. Fitting 50' will attach via fitting 52' to water pipe 54'. Water entry in this manner is intended as an example and is not intended to restrict the invention only this manner of water entry.

In a second alternate embodiment, depicted in FIGS. 10-13, and generally referenced as 100, the inner liner 120 terminates substantially even with outer shell 180. Spray ring 160 is angled between outer shell 180 and inner liner 120 so that passageways 280 direct water flow from volume 240 onto inner surface 200 of outer shell 180.

Directing the water flow from passageways 280 directly at the inner surface 200 of outer shell 180 intensifies the effect of the inwardly tapered inner surface 200. The water fans out from passageways 280 and collides with the inner surface of outer shell 180 and inwardly tapered inner surface 200 and is further broken up and/or dispersed into fine water particles. A portion of the water particles are deflected back onto the exterior surface 270 of inner liner 120 thereby providing a uniform film of water near the termination of the exterior surface 270 of inner liner 120. The uniform film of water absorbs heat from inner liner 120, and under certain operating conditions will almost instantaneously flash to steam thereby beginning the cooling process even prior to entering the turbulent cooling area 220.

Passageways 280 in spray ring 160, shown in FIGS. 10-12, are fewer, but larger in diameter than passageways 28 in spray ring 16, shown in FIG. 4, and are more closely spaced toward the hydrostatic top portion of the device to compensate for the change in hydrostatic pressure within volume 240 such that the volume of water exiting volume 240 provides a uniform volumetric flow of water around inner liner 120 thereby providing a uniform cooling effect. Fewer large diameter passageways also increases water flow and the cooling effect is thereby increased. Passageways 280 may also be spaced so that a number of streams of water fan out therefrom such that streams from adjacent passageways 280 intersect after contacting inner surface 200 of outer shell 180 thereby causing a portion of the water to deflect away from outer shell 180 and onto the outer surface 270 of inner liner 120. Accordingly, it is important that spray ring 160 is spaced a sufficient distance from the termination of the inner liner 120 and outer shell 180, and that passageways 280 are spaced and angled toward outer shell 180 so as to project fanning streams of water such that adjacent streams intersect after contacting outer shell 180 causing a portion of each water stream deflect onto the outer surface 270 of inner liner 120. In addition, a portion of the water disperses into a substantially uniform film on surface 200 of outer shell 180 and is dispersed as fine particles by the inwardly tapered inner surface 200 into the central region of the exhaust gas flow 220.

In this second alternate embodiment, inner liner 120 has an end portion which terminates at a point substantially even with the end portion of outer shell 180. As in the first embodiment, the inwardly tapered surface 140 of inner liner 120 clips turbulence and thus inhibits water from traveling backward along inner surface 260 of inner liner 120.

It has been found that the present invention functions optimally when sized to maintain the flow of exhaust gas at approximately 1.5 feet/second (approximately 75-80 miles per hour) relative to the velocity of the water. When operating under such conditions the present invention effectively reduces the exhaust gas temperature from inlet temperatures of approximately 700-1000.degree. F. to approximately 130-140.degree. F., while causing the cooling water, having an inlet temperature of approximately 100-120.degree. F., to vaporize into steam. The present invention is thus sized to maximize the cooling effect by causing substantially all of the cooling water to vaporize and be ejected from the exhaust system as steam vapor.

In use in a marine exhaust system the present embodiment 100 performs as follows. Water is supplied to the present invention, and as shown in FIG. 11 water will enter volume 240 inlet pipe 480. It should be recognized that any structure and/or method of injecting water into volume 240 is within the scope of the invention. Water will flow through volume 240 and exit passageways 280 whereby streams of water are directed toward inner surface 200 of outer liner 180 whereafter droplets of water flow along inner surface 200 while other droplets of water deflect onto the outer surface 270 of inner liner 120 and/or toward region 220. The water and exhaust gas exiting the device then mix in region 220 wherein the water is vaporized thereby causing the exhaust gas to substantially cool.

The instant invention has been shown and described herein in what is considered to be the most practical and preferred embodiment. It is recognized, however, that departures may be made therefrom within the scope of the invention and that obvious modifications will occur to a person skilled in the art.