BACKGROUND Numerous types of pumps have been developed for moving matter from one location to another. Typically, the physical and/or chemical nature ofthe material being moved by the pump plays an important role in pump efficacy. For example, the dredging industry commonly utilizes large centrifugal pumps for suction and movement of slurry material, i. e., water or other liquid in admixture with solid particulate matter, e. g., sand or gravel. Because of the abrasive characteristics of particles within such slurry material, these pumps typically suffer wear and tear and significant downtime to repair equipment components, especially moving parts which come into direct contact with the particulate matter.

Another dredging technique involves the use of air to induce an upward flow of water.

This technique has typically involved compressed air or gas, requiring expensive compression equipment. In addition, the combination of gas, water and solids has contributed to process instability in the mixing chamber of the device, as discussed in U. S. Patent No. 4,681,372.

Other hydraulic pumps employed in dredging and deep sea mining operations employ j et eduction systems, in which water is forced through piping configurations to cause an upward flow that pulls the water and solid material from the desired location. However, many jet eductor systems are flawed in that their high pressure water jets, while effective at removing high volumes of slurry material, cause severe cavitation in the throat and mixing regions of the

eductor conduit, and result in lowered efficiency and extremely short equipment life, as discussed in, e. g., U. S. Patent No. 4,165,571.

Other jet eduction systems have used atmospheric air for the purpose of creating air bubbles for separation processes, as in U. S. Patent No. 5,811,013. These systems are not designed to increase pump efficiency, prevent pump cavitation or increase pump flow as disclosed by the present invention. However, U. S. Patent 5,993,167 does disclose a jet eduction system which permits air to form a layer surrounding a high pressure flow of liquid, which is directed through a space and into a tube, thereby forming a vacuum in the space. Yet, this system does not produce vacuum sufficient for many commercial operations, and does not provide for control of the weight percentage of solids in pumped slurries.

Thus a need continues to exist for a commercially viable jet eduction system which moves large volumes of matter with very little wear and tear on the system. A need also exists for systems which enabling users to achieve greater pumping efficiency.

SUMMARY OF THE INVENTION The present invention overcomes the shortcoming of prior developments by providing, among other things, a pumping system which can (a) increase the quantity of material moved, relative to previously developed pumps, without an increase in energy consumption, (b) move solid materials with minimal wear on component parts, (c) overcome the problems associated with traditional venturi effect pumps, (d) include specific component parts which are designed to wear and which can be easily changed, (e) produce a vacuum for suctioning material with little or no cavitation, and/or (f) enable the control of the solid to liquid ratio of the material being pumped to drastically increase the pumping efficiency. Moreover, the present invention provides an efficient mixing system which employs a jet pump of this invention and enables users to

rapidly form a liquid and sol d material mixture, preferably one in which the mixture is substantially homogeneous, to control the weight percent of solids in the resulting mixture, and to efficiently transport the mixture downstream from the jet pump to a desired location.

Thus, in one embodiment of the present invention, an improved liquid jet pump is provided. The liquid jet pump is comprised of a nozzle assembly that pulls in atmospheric air.

The liquid jet created by passage of liquid through the nozzle assembly has minimal deflection as it exits because of an atmospheric air bearing surrounding the liquid jet. Consequently, the liquid jet pump has improved efficiency and capacity. The liquid jet pump is configured to define a suction chamber and further comprises a suction pipe. The suction pipe pulls in the material to be pumped as the liquid jet from the nozzle assembly passes through the suction chamber. The liquid jet pump further comprises a target tube that receives the liquid jet combined with material to be pumped which enters the suction chamber after traveling through the suction pipe. The target tube is comprised of a housing support detachable from the suction chamber and a wear plate of abrasion-resistant material.

In another embodiment, this invention provides apparatus which is comprised of (a) a nozzle assembly which is sized and configured to (i) receive a pressurized liquid and a gas, and (ii) eject the pressurized liquid as a liquid flow while feeding the gas into proximity with the periphery of the liquid flow; (b) a housing defining a suction chamber into which the nozzle assembly may eject the liquid flow, the housing also defining a suction inlet and a suction outlet; (c) an outlet pipe extending from the suction outlet away from the suction chamber housing, said outlet pipe being configured for liquid communication with the suction chamber and being disposed to receive the liquid flow; the outlet pipe defining at least a first inner diameter along a portion of its length and a second inner diameter along another portion of its length, the second inner diameter being less than the first inner diameter; and (d) a suction pipe, a first end of the

suction pipe opening into the suction chamber at the suction inlet, and a second end of the suction pipe opening into the surrounding environment; wherein the nozzle assembly extends into the suction chamber towards the suction outlet and into the imaginary line of flow of the suction pipe.

In another embodiment, this invention provides a pumping system comprising: (a) a nozzle assembly which is sized and configured to (i) receive a pressurized liquid and a gas, and (ii) eject the pressurized liquid as a liquid flow while feeding the gas into proximity with the periphery of the liquid flow; (b) a housing defining a suction chamber into which the nozzle assembly may eject the liquid flow, the housing further defining a suction inlet and a suction outlet; (c) an inlet pipe for providing pressurized liquid to the nozzle assembly; (d) a gas conduit for providing the gas to the nozzle assembly; (e) an outlet pipe extending from the suction outlet away from the suction chamber, the outlet pipe being configured for liquid communication with the suction chamber and being disposed to receive the liquid flow; the outlet pipe defining at least a first inner diameter along a portion of its length and a second inner diameter along another portion of its length, the second inner diameter being less than the first inner diameter; and (f) a suction pipe, a first end of the suction pipe opening into the suction chamber at the suction inlet, and a second end of the suction pipe opening into the surrounding environment. This invention also provides a system for dredging matter from the bottom of a body of water, the system comprising: (a) a pumping system as described above in this paragraph, (b) a buoyant platform equipped to raise and lower at least a portion of the pumping system relative to the bottom of the body of water, and (c) a first pump for providing the pressurized liquid to the nozzle assembly.

In yet another embodiment of the present invention, a method of moving, from one location to another, a slurry comprised of a solid and a liquid, is provided. The method

comprises: a. injecting a pressurized liquid into a nozzle assembly to produce a flow of pressurized liquid, b. providing a gas to the nozzle assembly to surround the flow of pressurized liquid with the gas, c. directing the flow of pressurized liquid surrounded by the gas into a suction chamber in fluid communication with an inlet pipe and an outlet pipe, the outlet pipe defining a venturi-like inner surface, and directing the flow of pressurized liquid surrounded by the gas toward the outlet pipe to produce a vacuum at a free end of the inlet pipe, and d. controlling the flow rate of the gas into said nozzle assembly to thereby control the weight ratio of solid to liquid in the slurry so moved.

These and other embodiments, objects, advantages, and features of this invention will be apparent from the following description, accompanying drawings and appended claims.

BRIEF DESCRIPTION OF THE DRAWINGS Figure 1 is a plan view of one preferred dredging assembly embodiment of this invention.

Figure 2 is a sectional view of the jet pump component of the assembly of Fig. 1.

Figure 3 is a sectional view of the jet pump components indicated on Fig. 2.

Figure 4A is a sectional view of a preferred embodiment of the nozzle assembly showing minimal deflection of the liquid jet.

Figure 4B is a sectional view of an embodiment of the nozzle assembly showing deflection of the liquid jet.

Figure 5 is a perspective view of material moving through the nozzle assembly and suction chamber.

Figure 6 is a perspective view of a preferred embodiment of the nozzle assembly, suction chamber and target tube of the invention.

Figure 7 and Figure 8 are sectional views of a preferred embodiment of the nozzle assembly of the invention.

Fig. 9 is a sectional view of another jet pump component of this invention which is an alternative to that illustrated in Fig. 2.

Figs. 10 and 11 are sectional views the nozzle assembly from the jet pump component of Fig. 9.

In each of the above figures, like numerals or letters are used to refer to like or functionally like parts among the several figures.

DETAILED DESCRIPTION OF THE INVENTION It will now be appreciated that, while specific embodiments are described hereinafter, several other applications of the presently described invention may be contemplated by those of skill in the art in view of this disclosure. For example, while the accompanying drawings illustrate the pumping system of this invention as used for dredging operations, the system may be used for virtually any application in which solid particulate matter, e. g., or a slurry comprised of such matter, must be moved from one location to another. The system also may be employed to remove liquids from such slurry mixtures, thereby permitting solid particulate matter to be rapidly separated from the liquid and dried, if desired. In each of the above examples, small batch operations as well as large commercial batch, semi-continuous and continuous operations are possible using pumping methods and systems of this invention.

The gas employed in the pumping systems and methods of this invention will preferably be under no more than atmospheric pressure, to reduce risk of operations and cost. The gas

preferably will be an inert gas, e. g., nitrogen or argon, when the liquid or other material being pumped could be volatile in the presence of certain atmospheric gases, e. g., oxygen. When such volatility is not an issue, the gas employed will be most conveniently atmospheric air.

Turning now to the drawings, Fig. 1 illustrates one preferred embodiment of this invention, in use on a barge 100 for dredging solid materials from a water source, such as a lake or river. Barge 100 is equipped with a cantilever system 101 to raise and lower a suction pipe 102 into the water source. Suction pipe 102 is connected to a jet pump 107 configured in accordance with this invention and further described hereinafter.

A discharge pipe 103 feeds water or other liquid pumped by a pump 104 to jet pump 107.

Pump 104 is typically a centrifugal pump, but can be any kind of pumping means, such as a positive displacement pump or even another jet pump. Pump 104 can be contained in a pump housing 105. Discharge pipe 103 also feeds water or other liquid to a supplemental jet nozzle assembly, illustrated here as a jet nozzle 106, upstream from jet pump 107 and suction pipe 102.

Jet nozzle 106 is sized and configured to project a pressurized liquid flow into the surrounding environment, to thereby break up solid material to facilitate its incorporation into the material pumped by jet pump 107.

Although suction pipe 102 is shown in Figure 1 as an angled inlet to j et pump 107 before becoming parallel to discharge pipe 103, suction pipe 102 can be any angle greater than 0° and less than 180 ° to discharge pipe 103 for all or any part of the length of suction pipe 102. A pump 108 can optionally be placed downstream of jet pump 107. Pump 108 is typically a centrifugal pump but can be any pumping means, as noted earlier for pump 104.

The depiction of the preferred embodiment of this invention for use in the dredging industry reflected in Figure 1 is only one illustrative example of the numerous applications in which embodiments of this invention may be employed. Jet pump 107, for instance, can vary

in size, from handheld unit to mounted on a bulldozer, mudbuggy or other vehicle, for use in various applications. The distance between pump 104 and jet pump 107, i. e., the length of the discharge pipe, can also vary greatly.

Figures 2 and 3 illustrates jet pump 107 in greater detail. Jet pump 107 includes nozzle assembly 307 (Figure 3 only), which in turn is comprised of a fluid nozzle 201, an air injection nozzle 202 and a nozzle housing 203. Nozzle housing 203 is a flanged member which is attached to and maintains the proper position of fluid nozzle 201 adjacent to air injection nozzle 202. Air intake 211 is one or more passages through nozzle housing 203. In the embodiment depicted, a single air intake 211 is shown although those skilled in the art could use more. A gas conduit in the form of an air hose 204 provides a gas to jet pump 107 and allows jet pump 107 to use air even when below the water level.

Water or other fluid supplied by a pumping means passes through discharge pipe 103, fluid nozzle 201, and air injection nozzle 202 into a housing 200 which defines a suction chamber 205. In suction chamber 205, the fluid in the form of a liquid flow combines with material entering from suction pipe 102, and the combined stream enters an outlet pipe 207 having a target tube 206. The combined stream then passes through target tube 206 into outlet pipe 207.

In a preferred embodiment jet nozzle 106 extends from discharge pipe 103, allowing a portion of the forced fluid supplied by pumping means to pass through jet nozzle 106. In a similar manner to the configuration for jet pump 107, jet nozzle 106 contains a venturi 209 at its end opposite the end connected to discharge pipe 103. Venturi 209 is equipped with air hose 204 to allow entry of atmospheric air when jet pump 107 is submerged.

Jet nozzle 106 extends approximately the same length as suction pipe 102 and, as depicted in Figure 1, terminates approximately 30.48 cm (one (1) foot) from the open end of

suction pipe 102. Fluid forced through jet nozzle 106 exits venturi 209 with air into the material that will be suctioned. An air bearing effect minimizes deflection and allows deeper penetration to loosen to the material being transferred. The jet stream also creates a churning effect that directs the churned material into the open end of suction pipe 102.

Although jet nozzle 106 is shown in Figures 1 and 2 as a single attachment, in an alternate embodiment, multiples of jet nozzle 106 can be attached to discharge pipe 103. In another embodiment, one or more jet nozzles 106 can be attached to suction pipe 102, handheld, or mounted on other equipment, depending on the application.

Referring to Figures 3,4A and 4B, in the interior of nozzle housing 203, fluid nozzle 201 includes constricted throat 301. Fluid nozzle 201 is attached by a connecting means to air injection nozzle 202. Air gap 302 exists between constricted throat 301 and air injection nozzle 202. In one embodiment, air gap 302 between constricted throat 301 and air injection nozzle 202 at its narrowest point measures ca. 0.48 cm (3/16 of an inch). The overall area and dimension at the narrowest point of air gap 302 will vary with the application and the material being transferred to optimize the suction effect.

Constricted throat 301 is attached to air injection nozzle 202 by means of nozzle housing 203. Nozzle housing 203 is a flanged pipe with air intake 211 drilled into the pipe circumference. Although nozzle housing 203 is depicted with one air intake 211, those skilled in the art would know that multiple air intakes can be provided.

Air injection nozzle 202 is provided with one or more air holes 304. In a preferred embodiment depicted in Figure 6, air injection nozzle 202 has eight 1.27 cm (1/2 inch) holes 304 equal distance around the circumference of air injection nozzle 202.

When air injection nozzle 202 and fluid nozzle 201 are assembled, one of air holes 304 can align with air intake 211. Alignment however is not necessary, as air injection nozzle 202

further defines an annular trough 602 in its outer surface into which air holes 304 open, thereby providing a path for air flow around the circumference of nozzle 202 and into each of holes 304.

Air hole 304 and air intake 211 allow the entry of atmospheric air to fill air gap 302. The forced delivery of liquid through constricted throat 301 creates a vacuum in air gap 302 that pulls in atmospheric air. Varying the amount of air entering air hole 304 creates an increased suction effect in air gap 302.

In one embodiment, vacuum in air gap 302 measured 73.66 cm (29 inches) Hg when air intake 211 was 10% open, compared to 25.4 cm (10 inches) Hg when air intake 211 was 100% open. Restriction of air though air intake 211 can be accomplished by any mechanical valve means.

Without being bound to theory, it is believed that entry of a gas (e. g., air) into air gap 302 creates a gas bearing effect. The air surrounds the flow of fluid leaving constricted throat 301 and the combined fluid jet with surrounding air passes through air injection nozzle 202.

Referring to Figures 2,3, and 5, the fluid jet with the air, introduced through air gap 302, exits air injection nozzle 202, passes through suction chamber 205, and enters target tube 206.

The combined air fluid jet passes through suction chamber 205 with minimal deflection before entering target tube 206.

As illustrated approximately in Figures 4A and 4B, a visual correlation can be observed between the deflection of a liquid jet entering target tube 206, and the presence of atmospheric air in air gap 302. Figure 4A shows the liquid pattern with atmospheric air creating air bearing 501. Figure 4B depicts the liquid pattern exiting air injection nozzle 202 without atmospheric air present. For the embodiment depicted, the best results for pumping only water were achieved when the pump discharge pressure was 1034.21-1206.58 kPa (150-175 p. s. i.) and the vaccum in air gap 302 was 45.72-55.88 cm (18-22 inches) of Hg.

Air bearing 501 around the liquid jet minimizes deflection, and thus, cavitation in suction chamber 205. Less cavitation reduces wear and the need to replace component parts, and increases flow through suction chamber 205 into target tube 206 with the liquid jet stream.

Referring to Figure 3, suction chamber 205 is shown with suction pipe 102 entering at a 45'angle. The design of suction chamber 205 allows one to adjust the placement of air injection nozzle 202 so that air injection nozzle 202 is out of the flow of solid material entering suction chamber 205, so as to prevent wear, or further into suction chamber 205 so as to create a greater vacuum.

Suction pipe 102 entering at an angle avoids the problem common to many eductor nozzles suffering excessive wear and corrosion by being placed in the flow of solid material.

Although this configuration is a preferred embodiment to maximize the entry of slurry material with minimal abrasive effect, those skilled in the art would know that alternate angles greater than 0° and less than 180° can be utilized.

In the embodiment depicted, suction chamber 205 measures ca 62.87 cm (243/4 inches) at A. The distance between nozzle opening 303 and one end of target tube 206 is ca 34.93 cm (133/4 inches) at B.

As the liquid jet passes through target tube 206, a suction effect is created in suction chamber 205. The suction effect pulls in any material located at open end of suction pipe 102.

The suction effect increases the overall quantity of material driven by pump 104. The following Table 1 illustrates the ratio of pumped liquid entering fluid nozzle 201 to total material exiting target tube 206:

Table 1 Pump Vacuum Liquid Exit Liquid Inlet Suction Ratio Discharge Discharge Measured In Power Fluid Nozzle Tube kPa Pressure Exit Pressure Air Gap liters per liters per [(psia) l kPa kPa cm Hg minute minute {(psia) [ (psia)] [ (inches Hg)] [ (gallons per {(gallons per minute)] minute) l ca 689.48 63. 5 11960. 6 2543. 52 ca 32.41 ca 41.37 [100] [25] [3160] [672] [4. 70] [6] ca 861. 85 63. 5 13247. 5 2952. 3 ca 30.96 ca 48.26 [125] [25] [3500] [780] [4.49] [7] 1034.21 63. 5 15707. 75 3118. 84 ca34.75 ca 55.16 [150] [25] [4150] [824] [5. 04] [8] 1206.58 63. 5 16881. 1 3368. 65 ca 34.54 ca 62.05 [175] [25] [4460] [890] [5.01] [9] 1378.78 63. 5 15442. 8 3595. 75 ca 29.58 ca 65.50 [200] [25] [4080] [950] [4.29] [9.5] 1551.32 63. 5 17032. 5 3785 ca 31.03 ca 65.50 [225] [25] [4500] [1000] [4.50] [9. 5] 1723.69 63. 5 17032. 5 ca 4023.46 ca 29.16 ca 68.95 [250] [25] [4500] [1063] [4.23] [10] ca689.48 50. 8 11884. 9 2543. 42 ca 32. 20 ca 41.37 [100] [20] [3140] [672] [4.67] [6] ca 861. 85 50. 8 14004. 5 2952. 3 ca32.68 ca 41.37 [125] [20] [3700] [780] [4.74] [6] 1034.21 50. 8 15329. 25 3118. 84 ca 33.92 ca 48.26 [150] [20] [4050] [824] [4.92] [7] 1206. 58 50. 8 15783. 45 3368. 65 ca 32.34 ca 55.16 [175] [20] [4170] [890] [4. 69] [8] 1378.95 50. 8 15707. 75 3595. 75 ca 30.13 ca 62.05 [200] [20] [4150] [950] [4.37] [9] 1551.32 50. 8 13626 3785 ca 24.82 ca 68.95 [225] [20] [3600] [1000] [3.60] [10] 1723.69 50. 8 12490. 5 ca 4023.46 ca 21.37 ca 68.95 [250] [20] [3300] [1063] [3. 10] [10] ca689.48 38. 1 13058. 25 2543. 42 ca 35. 37 ca 41.37 [100] [15] [3450] [672] [5.13] [6]

Pump Vacuum Liquid Exit Liquid Inlet Suction Ratio Discharge Discharge Measured In Power Fluid Nozzle TubekPa Pressure Exit Pressure Air Gap liters per liters kPa cm Hg minute minute (psia)] i (psia)] [ (inches Hg)] [ (gallons per [ (gallons: minute)] minute)] ca 861.85 38. 1 903441 2952. 3 ca 34.54 ca 41.37 [125] [15] [3911] [780] [5.01] [6] 1034.21 38. 1 933471 3118. 84 ca 33. 78 ca48.26 [150] [15] [4041] [824] [4.90] [7] 1206.58 38. 1 831600 3368. 65 ca27.85 ca 55.16 [175] [15] [3600] [890] [4. 04] [8] 1378.95 38. 1 739200 3595. 75 ca 23.24 ca 62.05 [200] [15] [3200] [950] [3.37] [9] 1551.32 38. 1 531300 3785 ca 15.86 ca 68.95 [225] [15] [2300] [1000] [2.30] [10] 1723.69 38. 1 623700 ca 4023.46 ca 17.51 ca 68.95 [250] [15] [2700] [1063] [2.54] [10] The specific gravity of the material pumped, i. e. water, versus sand or gravel, will affect the optimum inches vacuum in air gap 302 and the discharge pressure of pump 104. During testing of jet pump 107, vacuum in air gap 302 measured 73.66 cm (29 inches) Hg when suctioning water, 60.96 cm (24 inches) Hg when suctioning slurry material containing sand, and 45.72 cm (18 inches) Hg when suctioning material containing gravel.

The suction effect created by target tube 206 allows the movement of larger quantities of material without any concurrent increase in horsepower to operate pump 104 providing the liquid flow. For example, testing has demonstrated movement of material containing 60-65% by weight of sand, as compared to the 18-20% of solids using conventional methods such as centrifugal pumps at the same flow rate or discharge pressure.

Target tube 206 constitutes a segment of the outlet pipe in the form of a detachable wear plate in the preferred embodiment illustrated. The outlet pipe segment defines an inner surface,

at least a portion of which in turn defines the second inner diameter of the outlet pipe. The target tube can be detached from outlet pipe 207 and suction chamber 205. The majority of wear from abrasive material occurs in target tube 206, not suction chamber 205, because of reduced cavitation from the air bearing effect on the liquid jet and the design of suction chamber 205.

In Figures 3 and 6, target tube 206 is fixably attached to target tube housing 306. Once target tube 206 is worn, target tube 206 can be removed by detaching target tube housing 306 from suction chamber 205 on one end and outlet pipe 207 on the other end without having to open suction chamber 205.

In an alternative embodiment, target tube 206 may be fixably attached at one end to a connecting means such as a split locking flange. The split locking flange could then hold target tube 206 in place at one end by connecting between outlet pipe 207 or suction chamber 205 and target tube housing 306. The opposite end of target tube 206 could then rest on target tube housing 306 using notches or other means to prevent axial or radial movement.

A centrifugal pump 108, as shown in Figure 1, can be placed downstream of target tube 206 despite the introduction of atmospheric air before nozzle opening 203. No cavitation occurs in centrifugal pump 108 from the atmospheric air. This is counter to conventional wisdom regarding operation of centrifugal pumps by those skilled in the art. The atmospheric air likely dissolves in the liquid jet in or past target tube 206, further supporting the optimum effect observed when atmospheric air is restricted in its entry through air intake 211.

Target tube 206 can vary in both length and diameter. Diameter will most often be determined by the particle size of the material conveyed. Length and diameter of target tube 206 will effect the distance and head pressure that jet pump 107 can generate.

In a preferred embodiment shown in Figure 6, target tube 206 measures 91.44 cm (36 inches) in length, with ca 16.84 cm (6 % inches) outer diameter and 15.24 cm (6 inches) inner

diameter. Target tube housing 306 is composed of two 15.24 x 30.48 cm (6 x 12 inch) reducing flanges, each connected to one end of ca 32.39 cm (123/4 inch) pipe 25.4 cm (10 inches) long.

Interior target tube wear plate 305 (as shown in Figure 3) is composed of abrasion-resistant material such as, e. g., metals with high chrome content.

As shown in Figure 6, target tube 206 is a straight pipe with blunt edges. In an alternate embodiment shown in Figure 2, target tube 206 could have angled edges of a larger diameter than the diameter of the target tube body at one or both ends of target tube 206.

In a preferred embodiment, the nozzle elements of Figure 7 are constructed according to specific proportions. Although the nozzle elements are shown as three separate elements, those skilled in the art would know that the nozzle assembly could be constructed of one or more elements of varying dimensions. Fluid nozzle 201 is 12.7 cm (5 inches) in length and 20.32 cm (8 inches) in outer diameter. Constricted throat 301 of fluid nozzle 201 at inner edge 701 narrows radially inward from 20.32 cm (8 inches) to 5.08 cm (2 inches) diameter at its narrowest point at a 45 °angle. Constricted throat 301 measures 7.62 cm (3 inches) in diameter on outer edge 702.

Air injection nozzle 202 is ca 12.88 cm (127/8 inches) in length. At one end, air injection nozzle 202 is 25.4 cm (10 inches) in diameter on outside surface 703, and ca 20.35 cm (8.01 inches) in diameter on inside surface 704. Outside surface 703 remains 25.4 cm (10 inches) in diameter axially for a length of 12.7 cm (5 inches), then drops radially to a diameter of 17.78 cm (7 inches), and angles inward radially to a diameter of 10.16 cm (4 inches) for the remaining length. In a preferred embodiment, air injection nozzle 202 has an angle of 102° between the smallest diameter at angled end in the vertical plane and angled edge.

Inside surface 704 of air injection nozzle 202 remains ca 20.35 cm (8.01 inches) axially for a length of ca 10.64 cm (43/, inches), then drops radially to a diameter of 6.35 cm (2 1/2 inches) for the remainder of the length.

Air hole 303 is 1. 27 cm (1/2 inch) in diameter equally spaced along the circumference of outside surface 703 located 5.08 cm (2 inches) from the end of air injection nozzle 202 that has a 25.4 cm (10 inch) diameter.

In a preferred embodiment, nozzle housing 203 measures 34.29 cm (13 V2 inches) at flanged end 705 connected to fluid nozzle 201. At flanged end 706 connected to suction chamber 205, the outer diameter measures 48.26 cm (19 inches). Flanged end 705 has an inner diameter measures ca. 17.94 cm (7.0625 inches), sufficient to allow passage of air injection nozzle 202 at its angled end. Flanged end 705 has an inner diameter for the remaining length of ca. 25.43 cm (10.01 inches) to accommodate air injection nozzle 202 at its largest point. Nozzle housing 203 has a 2.54 (1 inch) NPT connection in air intake 211.

Figures 9,10 and 11 illustrate another preferred embodiment of the present invention.

This embodiment differs from the others illustrated in the previous figures in the configuration of the nozzle assembly and outlet pipe segment. As may be seen with reference to Figs. 10 and 11, the nozzle assembly of this particular embodiment is comprised of a fluid nozzle 401, an air pattern ring 402A, an air injection nozzle 402, and a nozzle housing 403. In this configuration, ring 402A can be replaced with modified rings when different air patterns are desired. Nozzle 402 is extended in length to permit the nozzle opening to be more proximate to target tube 406 (Fig. 9) without being so close to tube 406 so as to block larger particle size solids from passing from chamber 205 into tube 406. Surprisingly, it has been found that nozzle 402 may extend into the imaginary line of flow of suction pipe 102, represented on Fig. 9 with broken line Z, without suffering undue wear and tear as a result of solid material flowing into chamber 205. Thus,

increased vacuum may be achieved through nozzle extension without substantial adverse wear upon nozzle 402.

It will also be appreciated from Fig. 9 that the outlet pipe is comprised of a target tube (labeled 406 in Fig. 9) which defines a first inner diameter Q, the outlet pipe also defining a second inner diameter R which is less than inner diameter Q. However, outlet pipes of this invention may also be fabricated without a target tube but with a non-uniform inner surface so as to define a narrowing passage, so as to provide a venturi-like effect to the material exiting the suction chamber.

To further illustrate the present invention, a pump incorporating the features of that illustrated in Figs. 9-11 and having the following dimensions was employed to pump gravel, dirt and water from a gravel pit, and samples were taken to measure the percentage of solids which were pumped at various pressure settings. jet nozzle: inner diameter ("ID")-6.35 cm (2.5 inches), outer diameter ("OD")-ca.

14.92 cm (5 7/8 inches), length ("L")-ca. 17.94 cm (7 1/16 inches). air nozzle: ID-ca. 6.99 cm (2 3/4 inches), OD-10.16 cm (4 inches), L-43.18 cm (17 inches). air pattern ring: 3.81 cm (1.5 inches) width, ID-10.16 cm (4 inches), OD-ca. 14.92 cm (5 7/8 inches), having eight 1.27 cm (0.5 inch) diameter annularly displaced apertures about its circumference. outlet pipe segment: ID-17.78 cm (7 inches), L-90.17 cm (35.5 inches) and suction inlet ID- 30.48 cm (12 inches).

The settings during sampling and the results achieved are set forth in Table 2.

Table 2 Sample Jet Pump Dredge Pump Dredge Percent of Line Tons Jet Pressure Vacuum at Vacuum Pump Solids Velocity per upstream of nozzle air downstream Discharge (wt%) from Hour nozzle intake from Jet Pressure Dredge assembly (inches Hg) Pump (psia) Pump (psia) (inches Hg) (feet per second) 120 13 70 45 14 535 105 221 6 74 51 14 605 105 325 19 75 52 14 615 105 426 1 84 55 14 670 105 527 18 77 51 14 614 105 623 4 80 42 14 535 115 724 20 75 40 13 397 115 825 6 80 48 13 594 115 926 15 80 51 13 610 115 1027 21 75 46 14 550 115 1124 15 75 46 13 424 125 1226 15 80 52 14 667 120 It is believed that, heretofore, production of 18-20 wt% solids was the best that could be expected from conventional deck mounted dredging pumps. However, as can be seen from the data presented in Table 2, percentages at or above 40 wt% solids, and more preferably at or above 50 wt% solids, in the pumped material are routinely achieved. Such results are most readily achieved in particularly preferred embodiments of this invention by controlling gas flow so as to maintain gas entering the nozzle assembly under a vacuum in the range of 18 inches Hg to 26 inches Hg, and operating the dredge pump at an intake pressure/vacuum in the range of 5 inches Hg to 5 psia. Pumping systems of this invention operated under these conditions enable particularly drastic and surprising improvements in pumping efficiency.

While it is understood that at least one preferred jet pump described herein is characterized by the entry of atmospheric air and a detachable outlet pipe segment forming a wear plate, it is apparent that the foregoing description of specific embodiments can be readily adapted for various applications without departing from the general concept or spirit of this invention. Thus, for example, the inner surface of the outlet pipe (which provides the venturi effect feature of the outlet pipe) alternatively can be defined by the pipe itself, rather than a detachable wear plate, and/or the gas entering the nozzle assembly can be an inert gas, e. g., nitrogen. In addition, an efficient mixing system and method are provided by this invention, whereby the jet pump described herein is employed to mix a liquid with solid or slurry material to form a mixture, wherein the weight percent of solids in the mixture is controlled by controlling the air intake vacuum and the dredge pump intake pressure/vacuum as described above. Such mixing systems facilitate mixing volatile materials by simply using an inert gas for the gas intake at the nozzle assembly. Mixtures made in accordance with this system are particularly uniform and can be substantially homogenous, presumably on account of the forces applied to the liquid and solid material in, for example, the suction chamber of jet pumps of this invention.

These and other adaptions and modifications are intended to be comprehended within the range of equivalents of the presently disclosed embodiments. Terminology used herein is for the purpose of description and not limitation.

The present invention can be used in any application requiring significant suction effect of solid material in a liquid or gaseous environment. Those skilled in the art would know that the invention can also be used for suction in gaseous or liquid environments without solids present, and maintain a significant suction effect. Thus, as noted earlier, the invention can also be used in closed loop de-watering applications to remove excess water or moisture from material.

The dimensions of the various component parts of devices of this invention may vary depending upon the circumstances in which the device will be employed, so long as the dimensions permit the components to function as described herein. Except where specifically noted otherwise herein, the component parts may be fabricated from a wide variety of materials, the selection of which will depend again upon the circumstances in which the device will be employed. Preferably, metals, metal alloys or resilient plastics, for example, will be employed to insure that points of mechanical contact or abrasive wear in the systems and pumps will be resilient enough to withstand the forces placed upon them during pump operation.

This invention is susceptible to considerable variation in its practice. Therefore, the foregoing description is not intended to limit, and should not be construed as limiting, the invention to the particular exemplifications presented hereinabove. Rather, what is intended to be covered is as set forth in the ensuing claims and the equivalents thereof. As used in this specification, means-plus-function clauses are intended to cover the structures described herein as performing the cited function and not only structural equivalents but also equivalent structures.